WO2016094254A1 - Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes - Google Patents

Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes Download PDF

Info

Publication number
WO2016094254A1
WO2016094254A1 PCT/US2015/064087 US2015064087W WO2016094254A1 WO 2016094254 A1 WO2016094254 A1 WO 2016094254A1 US 2015064087 W US2015064087 W US 2015064087W WO 2016094254 A1 WO2016094254 A1 WO 2016094254A1
Authority
WO
WIPO (PCT)
Prior art keywords
carrier
ring
transmission
clutch
assembly
Prior art date
Application number
PCT/US2015/064087
Other languages
English (en)
Inventor
Joseph S. Vanselous
Shaun E. Mepham
Chester L. PARYS
Gordon MCINDOE
Raymond J. Haka
Andrew W. Phillips
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
Priority to CN201580072485.8A priority Critical patent/CN107110303A/zh
Priority to JP2017530122A priority patent/JP2017537285A/ja
Publication of WO2016094254A1 publication Critical patent/WO2016094254A1/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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0853—CVT using friction between rotary members having a first member of uniform effective diameter cooperating with different parts of a second member
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Definitions

  • a vehicle having a driveline including a continuously variable transmission allows an operator of the vehicle or a control system of the vehicle to vary a drive ratio in a stepless manner, permitting a power source of the vehicle to operate at its most efficient rotational speed.
  • Transmissions are becoming more complicated since the engine speed must be more precisely controlled to limit the fuel consumption and emissions of cars. Additionally transmission component speed and efficiency is equally important.
  • a continuously variable transmission comprising a stationary housing
  • a continuously variable transmission comprising a stationary housing (ground); an input shaft; a variator comprising a first ring assembly and a second ring assembly; a first planetary gearset comprising a first sun gear, a first set of planet gears coupled to the first sun, and drivingly engaged to a first ring gear, and a first carrier; a second planetary gearset comprising a second sun gear, a second set of planet gears coupled to the second sun and drivingly engaged to a second ring gear, and a second carrier; an output shaft; a first selectable torque transmitting device coupled to the second sun and to the stationary housing; a second selectable torque transmitting device coupled to the first carrier and to the input shaft; a third selectable torque transmitting device coupled to the second carrier and to stationary housing; wherein, the input shaft is fixedly connected with the first ring assembly, the second ring assembly is fixedly connected with the second ring gear and the first sun gear, the first carrier is drivingly engaged to the second carrier, the output
  • a continuously variable transmission comprising a stationary housing (ground); an input shaft; a variator comprising a first ring assembly and a second ring assembly; a first planetary gearset comprising a first sun gear, a first set of planet gears coupled to the first sun, and drivingly engaged to a first ring gear, and a first carrier; a second planetary gearset comprising a second sun gear, a second set of planet gears coupled to the second sun and drivingly engaged to a second ring gear, and a second carrier; an output shaft; a first selectable torque transmitting device coupled to the second ring gear and to ground; a second selectable torque transmitting device coupled to the first carrier and to the input shaft; and a third selectable torque transmitting device coupled to the first carrier and to ground; wherein the input shaft is fixedly connected with the first ring assembly of the variator, the second ring assembly is fixedly connected with the first ring gear and the second sun gear, the first sun gear is drivingly engaged to the second
  • the variator is a ball-type variator comprises; a carrier assembly rotatably supporting a plurality of pivoting axles rotatably disposed about the transmission axis; and the pivoting axles each further rotatably supporting a ball; wherein the first ring assembly and second ring assembly each comprise a ball contact area in continuous contact with each of the balls, and wherein the carrier assembly moves in controlled fashion through a small range of angles in order to cause the pivoting axles to change orientation, thus varying the variable speed ratio between the first ring assembly and second ring assembly.
  • the overall transmission speed ratio within a first forward range increases; the overall transmission speed ratio within a second forward range decreases; and the overall transmission speed ratio within a reverse range becomes more negative.
  • the overall transmission speed ratio in the first forward range and the second forward range is the same; the second selectable torque transmitting device can be synchronously engaged while in the first forward range; the first selectable torque transmitting device can be synchronously engaged while in the second forward range; and a fixed-ratio transmission operating mode, which transmits no power through the variator, is established by simultaneous application of the first selectable torque transmitting device and the second selectable torque transmitting device.
  • the transmission is capable of being utilized in both front wheel drive vehicles and rear wheel drive vehicles.
  • the transmission further comprises an optional fourth clutch which selectably connects any two of the first planetary gearset or second planetary gearset's rotating elements, thus causing all of the elements to rotate in unison, and establishing a third forward range.
  • the fourth clutch when the fourth clutch is engaged, the entire gearset rotates as a single unit, causing the transmission output speed to be equal to the variator output speed, extending the transmission overall ratio, and passing all of the input power through the variator to the output ring gear in a pure CVP range.
  • a continuously variable transmission comprising: a stationary housing; an input shaft; a variator comprising a first ring assembly and a second ring assembly; a first planetary gearset comprising a first sun gear, a first set of planet gears coupled to the first sun, and drivingly engaged to a first ring gear, and a first carrier; a second planetary gearset comprising a second sun gear, a second set of planet gears coupled to the second sun and drivingly engaged to a second ring gear, and a second carrier; and an output shaft; wherein the input shaft is fixedly connected with the first ring assembly, the second ring assembly is fixedly connected with the first sun gear and the second sun gear, the second carrier is drivingly engaged to the first ring gear, the output shaft is drivingly connected to the first ring gear, and the variator controls a variable speed ratio between speeds of the first ring assembly and second ring assembly, thereby adjusting an overall transmission speed ratio.
  • a continuously variable transmission comprising: an input shaft operably coupleable to a source of rotational power; a variator assembly comprising a first traction ring assembly and a second traction ring assembly in contact with a plurality of balls, each ball having a tiltable axis of rotation; a first planetary gearset comprising a first sun gear, a first carrier, and a first ring gear; a second planetary gearset comprising a second sun gear, a second carrier, and a second ring gear; and an interfacing shift sleeve assembly comprising a first interfacing clutch and a second interfacing clutch; wherein the first traction ring assembly is coupled to the input shaft, the second traction ring assembly is coupled to the first sun gear and the second sun gear, the first interfacing clutch selectably couples the first ring gear to the second carrier, and the second interfacing clutch selectably couples the second ring gear to the first carrier.
  • the first interfacing clutch and the second interfacing clutch comprise dog clutches.
  • the continuously variable transmission further comprises a first selectable clutch coupled to the first ring gear, wherein the first selectable clutch selectably couples the first ring gear to a non-rotating housing.
  • the continuously variable transmission further comprises a second selectable clutch coupled to the input shaft, wherein the second selectable clutch selectably couples the input shaft to the second carrier.
  • a power output is transmitted through the second ring gear.
  • the first selectable clutch or the second selectable clutch comprises friction clutches.
  • the interfacing shift sleeve assembly is located radially outward of the first planetary gear set and the second planetary gear set.
  • the interfacing shift sleeve assembly comprises a plurality of internal teeth configured to selectably engage mating surfaces on the first ring gear and the second ring gear. In some embodiments, the interfacing shift sleeve assembly comprises a plurality of internal teeth configured to selectably engage mating surfaces on the first carrier and the second carrier. In some
  • an engagement of the interfacing shift sleeve assembly with the first ring gear corresponds to the engagement of the interfacing shift sleeve assembly with the second carrier. In some embodiments, an engagement of the interfacing shift sleeve assembly with the second ring gear corresponds to the engagement of the interfacing shift sleeve assembly with the first carrier.
  • the transmission further comprises an output shaft. In some embodiments, the transmission further comprises a second rotatable shaft coupled to the output shaft and the second ring gear. In some embodiments, the output shaft is operably coupled to a differential. In some embodiments, the transmission further comprises a power input interface. In some embodiments the power input interface comprises a torque converter.
  • a continuously variable transmission comprising: an input shaft operably coupleable to a source of rotational power; a variator assembly comprising a first traction ring assembly and a second traction ring assembly in contact with a plurality of balls, each ball having a tiltable axis of rotation; a first planetary gearset comprising a first sun gear, a first carrier, and a first ring gear; a second planetary gearset comprising a second sun gear, a second carrier, and a second ring gear; and an interfacing shift sleeve assembly comprising a first interfacing clutch and a second interfacing clutch; wherein the first traction ring assembly is coupled to the input shaft, the second traction ring is coupled to the first sun gear, the second traction ring assembly is coupled to the second sun gear and the interfacing shift sleeve assembly.
  • the first interfacing clutch selectably couples the first ring gear to the second carrier. In some embodiments, the second interfacing clutch selectably couples the second ring gear to the first carrier. In some embodiments, the first interfacing clutch and the second interfacing clutch comprise dog clutches.
  • the transmission further comprises a direct coupling to the source of rotational power.
  • the transmission further comprises an interfacing shift sleeve assembly comprising a first interfacing clutch and a second interfacing clutch wherein one or both of the first interfacing clutch and the second interfacing clutch comprise a dog clutch.
  • the variator comprises a traction fluid.
  • a vehicle driveline comprising a power source and any of the variable transmissions described herein; drivingly engaged with the power source, and a vehicle output drivingly engaged with the variable transmission.
  • the power source is drivingly engaged with the vehicle output.
  • a method comprising providing a vehicle driveline comprising any of the variable transmissions described herein.
  • Figure 1 is a stick diagram of a rear wheel drive embodiment of the 3-mode transmission as described herein.
  • Figure 2 is a stick diagram of a front wheel drive embodiment of the 3-mode transmission as described herein.
  • Figure 3 is a lever diagram of an embodiment of the 3-mode transmission as described herein.
  • Figure 4 is a lever diagram of another embodiment of the 3-mode transmission showing an optional sync clutch, as described herein.
  • Figure 5 is an alternate configuration view of the compound gear set of the 3-mode transmission.
  • Figure 6 is another alternate configuration view of the compound gear set of the 3-mode transmission.
  • Figure 7A is a side sectional view of one embodiment of a ball-type variator.
  • Figure 7B is a side sectional view of another embodiment of a ball-type variator.
  • Figure 7C is a plan view of a carrier member that can be used in the variator of Figure 7B.
  • Figure 8 is a magnified, side sectional view of a ball of a variator of Figure 7A having a symmetric arrangement of a first ring assembly and a second ring assembly.
  • Figure 9 is a variant block diagram of an embodiment of the 3-mode transmission as described herein.
  • Figure 10 is a lever diagram of the embodiment of the 3-mode transmission as described in FIG. 9.
  • Figure 11 is a stick diagram of the embodiment of the 3-mode transmission described in FIG. 9.
  • Figure 12 is a variant block diagram of an embodiment of the 3-mode transmission as described herein.
  • Figure 13 is a lever diagram of the embodiment of the 3-mode transmission as described in FIG. 12.
  • Figure 14 is a stick diagram of the embodiment of the 3-mode transmission described in FIG. 12.
  • Figure 15 is a variant block diagram of an embodiment of the 3-mode transmission as described herein.
  • Figure 16 is a lever diagram of the embodiment of the 3-mode transmission as described in FIG. 15.
  • Figure 17 is a stick diagram of the embodiment of the 3-mode transmission described in FIG. 15.
  • Figure 18 is a stick diagram of an embodiment of a 3-mode transmission with a sliding coupling and double-dog clutch for a Rear Wheel Drive configuration as described herein.
  • Figure 19 is a stick diagram of an embodiment of a 3-mode transmission with an axially located sliding coupling for a Front Wheel Drive configuration as described herein. DETAILED DESCRIPTION OF THE INVENTION
  • the continuously variable transmission speed ratio can have the advantage of providing a smoother and continuous transition from a low speed ratio to a high speed ratio.
  • the prior continuously variable transmissions can be more complex than would be ideal.
  • continuously variable transmissions have been proposed to provide vehicles with continuously variable speed transmissions having designs that avoid high pinion and/or carrier speeds and other disadvantages of existing 3 -mode power flows.
  • Continuously Variable Transmissions or CVTs comprise many types: belts with variable pulleys, toroidal, and conical, for non-limiting example.
  • the principle of a CVT is that it enables the engine to run at its most efficient rotation speed by changing steplessly the transmission ratio in function of the speed of the car and the torque demand (throttle position) of the driver. If needed, for example when accelerating, the CVT is configured to also shift to the most optimum ratio providing more power.
  • a CVT is configured to change the ratio from the minimum to the maximum ratio without any interruption of the power transmission, as opposed to the opposite of usual transmissions which require an interruption of the power transferred.
  • CVTs based on a ball type variators, also known as CVP, for constant variable planetary.
  • Basic concepts of a ball type Continuously Variable Transmissions are described in US20060084549 and AU2011224083A1, and 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) 997, depending on the application, two ring (disc) assemblies with a conical surface contact with the balls, as input traction ring 995 and output traction ring 996, and an idler (sun) assembly 999 as shown on FIG. 7A.
  • the balls are mounted on axes 998, themselves held in a carrier (stator, cage) assembly allowing for changing of the ratio between the input ring and the output ring by tilting the balls' axes.
  • 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 contact with the balls, as input traction ring 2 and output traction ring 3, and an idler (sun) assembly 4 as shown on FIG. 7B.
  • 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 can rotate with respect to the second carrier member 7, and vice versa.
  • the first carrier member 6 is optionally 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 optionally provided with a number of radially offset guide slots 9, as illustrated in FIG. 7C.
  • the radial guide slots 8 and the radially offset guide slots 9 are adapted to guide the tiltable axles 5.
  • the axles 5 are optionally 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, like the one disclosed by Milner, but are slightly different.
  • FIG. 8 The working principle of such a CVP of FIG. 7A is shown on FIG. 8.
  • the CVP itself works with a traction fluid.
  • the traction fluid 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 can be changed between input and output.
  • the ratio is one, 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 of the invention 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 optionally adjusted to achieve a desired ratio of input speed to output speed during operation.
  • adjustment of the 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”.
  • the tilting of the planet axis of rotation adjusts the speed ratio of the variator.
  • ring As used herein, the term "ring”, “ring assembly”, “rotating element of the variator assembly”, “traction ring” or “traction ring assembly” are interpreted to be the same thing by those skilled in the art.
  • 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,” 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 the terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of the terms is used, the term indicates that the actual linkage or coupling can take a variety of forms, which in certain instances will be readily apparent to a person of ordinary skill in the relevant technology.
  • 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
  • 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 force per contact force.
  • friction drives generally relate to transferring power between two elements by frictional forces between the elements.
  • the CVTs described here are capable of operating in both tractive and frictional applications.
  • the CVT is capable of operating at times as a friction drive and at other times as a traction drive, depending on the torque and speed conditions present during operation.
  • a lever diagram also known as a lever analogy diagram, is a translational-system representation of rotating parts for a planetary gear system.
  • a lever diagram is provided as a visual aid in describing the functions of the transmission.
  • a compound planetary gear set is often represented by a single vertical line ("lever").
  • the input, output, and reaction torques are represented by horizontal forces on the lever.
  • the lever motion, relative to the reaction point, represents direction of rotational velocities.
  • a front wheel drive or rear wheel drive continuously variable transmission configured to optimize speed ratios to provide good, tunable overall ratios (OAR) and mode overlap, while avoiding the high pinion or carrier speeds and other disadvantages of existing 3 -mode power flows.
  • a front wheel drive (or rear wheel drive) continuously variable transmission 10 comprising a stationary housing (ground), an input shaft 70, an output shaft 80, a gearset having a first rotating element 61, a second rotating element 63, a third rotating element 66, and a fourth rotating element 62, a variator assembly 30 having first and second rotating elements, a first selectable torque transmitting device ("first clutch") 21, a second selectable torque transmitting device (“second clutch”) 22, and a third selectable torque transmitting device (“third clutch”) 23; wherein the input shaft 70 is fixedly connected with the first rotating element of the variator assembly 30, the second rotating element of the variator assembly 30 is fixedly connected with the first rotating element 61 of the gearset, the output shaft 80 is fixedly connected with the third rotating element 66 of the gearset; the first clutch 21 connects the fourth rotating element 62 of the gearset to ground, establishing a first forward variable range of overall transmission speed ratios; the second clutch 22 connects the
  • the gearset is a complex planetary arrangement constructed from a simple and a compound planetary gearset having rotating elements comprising a first (simple or "single-pinion") planetary gearset 40 comprising; a first ring gear 41, a first sun gear 42, and a first carrier assembly 43, and, a second (compound or "double-pinion") planetary gearset 50, having rotating elements comprising; a second ring gear 51, a second sun gear 52, and a second carrier assembly 53; wherein the first carrier assembly 43 of the first planetary gearset 40 rotatably supports a first single set of pinions 44 which engage the single -pinion planetary gearset first ring gear 41 and the single-pinion planetary gearset first sun gear 42; and, the second carrier assembly 53 of the double-pinion planetary gearset 50 rotatably supports, a second set of pinions 54 which engage the double- pinion planetary gearset second sun gear 52, and a third set
  • the gearset is a compound
  • (Ravigneaux) planetary gearset 60 comprising a ring gear 66, a carrier assembly 63 rotatably supporting an outer set of long pinion gears 64 in mesh with the ring gear 66 and an inner set of short pinion gears 65 in mesh with the outer set of long pinion gears 64, a first sun gear 61 meshing with the outer set of long pinion gears 64, and a second sun gear 62 meshing with the inner set of short pinion gears 65; and wherein, the first rotating element of the gearset is the first sun gear 61, the second rotating element of the gearset is the carrier assembly 63, the third rotating element of the gearset is the ring gear 66, and the fourth rotating element of the gearset is the second sun gear 62.
  • the gearset 60 is a Ravigneaux compound planetary gearset.
  • a variator is a system that uses a set of rotating and tilting balls in a carrier that is positioned between an input ring and an output ring. Tilting the balls changes their contact diameters and varies the speed ratio. Contacting a rotating sphere at two different locations relative to the sphere's rotational axis will provide a "gear ratio", which can range from underdrive to overdrive depending on the location of the contact points for input and output torque and speed. As a result, the variator system offers continuous transition to any ratio within its range. The gear ratio is shifted by tilting the axes of the spheres in a continuous fashion, to provide different contact radii, which in turn drive the input and output rings, or discs.
  • the variator has multiple balls to transfer torque through multiple fluid patches.
  • the balls are placed in a circular array around a central idler (sun) and contact separate input and output traction rings at engagement points about the balls.
  • This configuration allows the input and output to be concentric and compact. The result is the ability to sweep the transmission through the entire ratio range smoothly, while in motion, under load, or stopped.
  • the variator itself works with a traction fluid.
  • the traction fluid is located in the variator for lubrication and traction.
  • This fluid undergoes high contact pressures under rolling contact between the two very hard elements, the balls and the rings, the fluid undergoes a near- instantaneous phase transition to an elastic solid.
  • This is also known as elastohydrodynamic lubrication (EHL).
  • EHL elastohydrodynamic lubrication
  • the molecules of the fluid stack up and link to form a solid, through which shear force and thus torque can be transferred. Note that the rolling elements are actually not in physical contact when the elements are rotating.
  • the traction fluid between the ball and the conical rings acts as a solid at high pressure, transferring the power from the first ring assembly 32 (input of the variator), through the variator balls 35, to the second ring assembly 33 (output of the variator).
  • the ratio is changed between input and output.
  • the ratio is one, when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio, between underdrive and overdrive. All the variator balls' axles are tilted at the same time and same angle with a mechanism included in the cage.
  • continuously variable transmission as described herein can be used in many applications such as bicycles, motorized vehicles, wind turbines, and power tools, for example.
  • the embodiments of the present invention as described herein will find applications in front-wheel drive or rear-wheel drive transmissions for both On- and Off-highway vehicles.
  • the variator is a ball-type variator 30 comprising; a carrier assembly 31 rotatably supporting a plurality of pivoting axles 34 rotatably disposed about the transmission axis, the pivoting axles 34 each in turn further rotatably supporting a ball 35; and wherein the first ring assembly 32 and the second ring assembly 33, each comprise a ball contact area in continuous contact with all of the balls 35.
  • the first rotating element of the variator 30 is the first ring assembly 32
  • the second rotating element of the variator 30 is the second ring assembly 32
  • the carrier assembly 31 moves in controlled fashion through a small range of angles as previous illustrated in FIG. 8, with respect to the variator housing in order to cause the pivoting axles 34 to change orientation, and thereby change the speed ratio between the first ring assembly 32 and the second ring assembly 33.
  • the first and second rotating elements of the variator assembly 30 are the first traction ring 32 and the second traction ring 33. In some embodiments, the first and second rotating elements of the variator assembly 30 are the first traction ring 32 and the carrier assembly 34.
  • the overall transmission speed ratio within a first forward range increases; the overall transmission speed ratio within a second forward range decreases; and the overall transmission speed ratio within a reverse range becomes more negative.
  • the transmission having a variator speed ratio which is near the upper end of the variator speed ratio range but still within the overall transmission speed ratio range, may have overall transmission speed ratios in the first and second forward ranges that are the same; wherein the second clutch can be synchronously engaged while in the first forward range; the first clutch can be synchronously engaged while in the second forward range; and an additional, fixed-ratio transmission operating mode, which transmits no power through the variator, is established by simultaneous application of the first and second clutches.
  • the fixed ratio operating mode is further described as the intersection of the 1st and 2nd modes; wherein, if both the first clutch and the second clutch are locked, then the variator in theory doesn't need to transmit any power.
  • the transmissions may further comprise an optional fourth clutch 24 which selectably connects any two of the four rotating elements of the planetary gearset 60, thus causing all of the elements to rotate in unison, and establishing a third forward range.
  • the planetary gearset 60 rotates as a single unit, thereby causing the transmission output speed to be equal to the variator output speed, extending the transmission overall ratio, and passing all of the input power through the variator to the ring gear 66 in a pure CVP range between 0.5 and 1.8, for illustrative example.
  • continuously variable transmission configurations described herein utilize two simple planetary gearset assemblies instead of a compound planetary gearset assembly.
  • a continuously variable transmission 100 comprising a stationary housing (ground); an input shaft 70; the variator 30 comprising the first ring assembly 32 and the second ring assembly 33; a first planetary gearset 140 comprising a first sun gear 142, a first set of planet gears 144 coupled to the first sun gear 142, and drivingly engaged to a first ring gear 141, and a first carrier 143; a second planetary gearset 150 comprising a second sun gear 152, a second set of planet gears 154 coupled to the second sun gear 152 and drivingly engaged to a second ring gear 151, and a second carrier 153; the output shaft 80; a first selectable torque transmitting device 161, a second selectable torque transmitting device 162, and a third selectable torque transmitting device 163; wherein, the input shaft 70 is fixedly connected with the first ring assembly 32 of the variator 30; the second ring assembly 33 of the variator is fixedly connected with the
  • the three selectable torque transmitting devices comprise: a first brake 161; a clutch 162; and a second brake 163.
  • a continuously variable transmission 110 comprising a stationary housing (ground); the input shaft 70; the variator 30 comprising the first ring assembly 32 and the second ring assembly 33; the first planetary gearset 140 comprising the first sun gear 142, the first set of planet gears 144 coupled to the first sun gear 142, and drivingly engaged to the first ring gear 141, and the first carrier 143; the second planetary gearset 150 comprising the second sun gear 152, the second set of planet gears 154 coupled to the second sun gear 152 and drivingly engaged to the second ring gear 151, and the second carrier 153; the output shaft 80; the first selectable torque transmitting device 161, the second selectable torque transmitting device 162, and the third selectable torque transmitting device 163; wherein, the input shaft 70 is fixedly connected with the first ring assembly 32 of the variator; the second ring assembly 32 of the variator is fixedly connected with the second ring gear 153 and the first sun gear 142;
  • a continuously variable transmission 120 comprising a stationary housing (ground); the input shaft 70; the variator 30 comprising the first ring assembly 32 and the second ring assembly 33; the first planetary gearset 140 comprising the first sun gear 142, the first set of planet gears 144 coupled to the first sun gear 142, and drivingly engaged to the first ring gear 141, and the first carrier 143; the second planetary gearset 150 comprising the second sun gear 152, the second set of planet gears 154 coupled to the second sun gear 152 and drivingly engaged to the second ring gear 151, and the second carrier 153; the output shaft 80; the first selectable torque transmitting device 161, the second selectable torque transmitting device 162, and the third selectable torque transmitting device 163; wherein, the input shaft 70 is fixedly connected with the first ring assembly 32 of the variator 30; the second ring assembly 33 of the variator 30 is fixedly connected with the first ring gear 141 and the second sun gear
  • the three selectable torque transmitting devices comprise: a first brake 161; a clutch 162; and a second brake 163.
  • the variator 30 is a ball-type variator comprising a carrier assembly rotatably supporting a plurality of pivoting axles 34 rotatably disposed about the transmission axis; the pivoting axles each further rotatably supporting a ball 35; and wherein the first ring assembly 32 and second ring assembly 33 each comprise a ball contact area in continuous contact with all of the balls, and wherein the carrier assembly moves in controlled fashion through a small range of angles with respect to the variator housing in order to cause the pivoting axles to change orientation, thus changing the speed ratio between the first and second rings assemblies.
  • the overall transmission speed ratio within the first forward range increases; the overall transmission speed ratio within the second forward range decreases; and the overall transmission speed ratio within the reverse range becomes more negative.
  • the overall transmission speed ratios in the first and second forward ranges are the same; the second selectable torque transmitting device can be synchronously engaged while in the first forward range; the first selectable torque transmitting device can be synchronously engaged while in the second forward range; and an additional, fixed-ratio transmission operating mode, which transmits no power through the variator, is established by simultaneous application of the first and second selectable torque transmitting device.
  • the transmission is capable of being utilized in both front wheel drive and rear wheel drive vehicles.
  • the transmission further comprises an optional fourth clutch which selectably connects any two of the first planetary gearset or second planetary gearset' s rotating elements, thus causing all of the elements to rotate in unison, and establishing a third forward range.
  • the entire gearset rotates as a single unit, causing the transmission output speed to be equal to the variator output speed, extending the transmission overall ratio, and passing all of the input power through the variator to the output ring gear in a pure CVP range.
  • continuously variable transmission 200 comprising a stationary housing (ground) 20, the input shaft 70, the variator 30 comprising the first ring assembly 32 and the second ring assembly 33, the first planetary gearset 40 comprising the first sun gear 42, the first set of planet gears coupled to the first sun gear 42, and drivingly engaged to the first ring gear 41, and the first carrier 43 configured to support the first set of planet gears, a second planetary gearset 90 comprising a second sun gear 92, a second set of planet gears coupled to the second sun gear 92 and drivingly engaged to a second ring gear 91, a second carrier 93 configured to support the second set of planet gears, and the output shaft 80, wherein, the input shaft 70 is fixedly connected with the first ring assembly 32 of the variator 30, the second ring assembly 33 of the variator 30 is fixedly connected with the first sun gear 42 and the second sun gear 92, the second carrier 93 is drivingly engaged to the first ring gear 41 and the output shaft 80 is drivingly connected to the first ring gear 41, where
  • a continuously variable transmission 200 comprising the input shaft 70 operably coupleable to a source of rotational power 25, the variator assembly 30 comprising the first traction ring assembly 32 and the second traction ring assembly 33 in contact with the plurality of balls 35, each ball 35 having a tiltable axis of rotation 34, wherein the first traction ring assembly 32 is coupled to the input shaft 70; the first planetary gearset 40 comprising the first sun gear 42, the first carrier 43, and the first ring gear 41, wherein the second traction ring assembly 33 is coupled to the first sun gear 42; the second planetary gearset 90 comprising the second sun gear 92, the second carrier 93, and the second ring gear 91, wherein the second traction ring assembly 33 is coupled to the second sun gear 91; an interfacing shift sleeve assembly 250 comprising a first interfacing clutch 261 and a second interfacing clutch 262, wherein the first interfacing clutch 261 selectably couples the first ring gear 41 to the second
  • the first and second interfacing clutches 261, 262 comprise dog clutches.
  • the continuously variable transmission further comprises a first selectable clutch 271 coupled to the first ring gear 41, wherein the first selectable clutch 271 selectably couples the first ring gear 41 to a non-rotating housing 20.
  • the continuously variable transmission further comprises a second selectable clutch 272 coupled to the input shaft 70, wherein the second selectable clutch 272 selectably couples the input shaft 70 to the second carrier 93.
  • a power output is transmitted through the second ring gear 91.
  • the first selectable clutch 271 or the second selectable clutch 272 comprises friction clutches.
  • the continuously variable transmission is configured for a rear wheel drive vehicle.
  • the interfacing shift sleeve assembly 252 is located radially outward of the first planetary gear set 40 and the second planetary gear set 90. [0090] In some embodiments of the continuously variable transmission, the interfacing shift sleeve assembly 252 comprises a plurality of internal teeth configured to selectably engage mating surfaces on the first ring gear 41 and the second ring gear91.
  • the interfacing shift sleeve assembly 252 comprises a plurality of internal teeth configured to selectably engage mating surfaces on the first carrier 43 and the second carriers93.
  • an engagement of the interfacing shift sleeve assembly 252 with the first ring gear 41 corresponds to the engagement of the interfacing shift sleeve assembly 252 with the second carrier 93.
  • an engagement of the interfacing shift sleeve assembly 252 with the second ring gear 91 corresponds to the engagement of the interfacing shift sleeve assembly 252 with the first carrier 43.
  • the continuously variable transmission further comprises an output shaft 80.
  • the continuously variable transmission further comprises a second rotatable shaft 72 coupled to the output shaft 80 and the second ring gear 91.
  • the continuously variable transmission further comprises a power input interface 15.
  • the power input interface 15 comprises a torque converter.
  • the continuously variable transmission is configured for a front wheel drive vehicle.
  • a continuously variable transmission 300 comprising the input shaft 70 operably coupleable to a source of rotational power 25; the variator assembly 30 comprising the first traction ring 32 and the second traction ring 33 in contact with a plurality of balls s 35, each ball 35 having a tiltable axis of rotation 34, wherein the first traction ring assembly 32 is coupled to the input shaft 70; the first planetary gearset 40 comprising the first sun gear 42, the first carrier 43, and the first ring gear 41, wherein the second traction ring assembly 33 is coupled to the first sun gear 42; the second planetary gearset 90 comprising the second sun gear 92, the second carrier 93, and the second ring gear 91, wherein the second traction ring assembly 33 is coupled to the second sun gear 92 and the interfacing shift sleeve assembly 252 comprising the first interfacing clutch 261 and the second interfacing clutch 262.
  • the first interfacing clutch 261 selectably couples the first ring gear 41 to the second carrier 93.
  • the second interfacing clutch 262 selectably couples the second ring gear 91 to the first carrier 43.
  • the first interfacing clutch 261 and the second interfacing clutch262 comprise dog clutches.
  • the continuously variable transmission comprises a direct coupling to the source of rotational power 25.
  • the transmission further comprises a direct coupling to the source of rotational power.
  • the transmission further comprises an interfacing shift sleeve assembly comprising a first interfacing clutch and a second interfacing clutch wherein one or both of the first interfacing clutch and the second interfacing clutch comprise a dog clutch.
  • the variator comprises a traction fluid.
  • a vehicle driveline comprising a power source and any of the variable transmissions described herein; drivingly engaged with the power source, and a vehicle output drivingly engaged with the variable transmission.
  • the power source is drivingly engaged with the vehicle output.
  • a vehicle comprising any of the variable transmissions described herein.
  • a method comprising providing a vehicle driveline comprising any of the variable transmissions described herein.
  • a method comprising providing a vehicle comprising any of the variable transmissions described herein.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

La présente invention concerne une transmission à variation continue pour l'entraînement des roues avant et des roues arrière, comprenant un arbre d'entrée, un arbre de sortie, un variateur planétaire à billes à inclinaison à variation continue, un ensemble train d'engrenages planétaires composé comportant un premier, un deuxième, un troisième et un quatrième élément rotatif, ainsi qu'une pluralité de dispositifs de transmission de couple. L'ensemble train d'engrenages planétaires composé comporte un seul train d'engrenages à pignon simple et un train d'engrenages à pignon double composé ayant des porte-planétaires raccordés fixement ainsi que des couronnes raccordées fixement, ce qui permet d'obtenir un porte-satellite à joint et une couronne à joint. Les engrenages planétaires externes s'engrènent avec la couronne qui entraîne l'arbre de sortie. Des dispositifs de transmission de couple sélectifs comprennent des embrayages et des embrayages de freinage. Des variantes de configurations de transmission à variation continue ayant recours à deux ensembles de jeux d'engrenage planétaire simples au lieu d'un agencement planétaire composé avec et sans variation de configurations de dispositif de transmission de couple.
PCT/US2015/064087 2014-12-08 2015-12-04 Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes WO2016094254A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580072485.8A CN107110303A (zh) 2014-12-08 2015-12-04 3‑模式前轮驱动和后轮驱动的无级行星变速器
JP2017530122A JP2017537285A (ja) 2014-12-08 2015-12-04 ３モードの前輪駆動および後輪駆動用の遊星機構無段変速機

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201462089126P 2014-12-08 2014-12-08
US62/089,126 2014-12-08
US201562144751P 2015-04-08 2015-04-08
US62/144,751 2015-04-08

Publications (1)

Publication Number Publication Date
WO2016094254A1 true WO2016094254A1 (fr) 2016-06-16

Family

ID=56108003

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2015/064087 WO2016094254A1 (fr) 2014-12-08 2015-12-04 Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes

Country Status (3)

Country Link
JP (1) JP2017537285A (fr)
CN (1) CN107110303A (fr)
WO (1) WO2016094254A1 (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US9638301B2 (en) 2013-03-14 2017-05-02 Dana Limited Ball type continuously variable transmission
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9644530B2 (en) 2013-02-08 2017-05-09 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9689477B2 (en) 2012-09-07 2017-06-27 Dana Limited Ball type continuously variable transmission/infinitely 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
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
WO2019036324A1 (fr) * 2017-08-14 2019-02-21 Dana Limited Groupes motopropulseurs comportant une transmission à variation continue de type à billes et un train planétaire de ravigneaux

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11485225B2 (en) * 2019-02-20 2022-11-01 Team Industries, Inc. Drivetrain layout with CVT
CN113474578B (zh) * 2019-03-12 2024-07-19 西格玛动力总成股份有限公司 变速器组件及其使用方法
US10948054B2 (en) * 2019-04-16 2021-03-16 Deere & Company Multi-mode integrated starter-generator device with solenoid cam actuation apparatus

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140194242A1 (en) * 2012-09-07 2014-07-10 Dana Limited Ball type cvt/ivt including planetary gear sets
WO2014179717A1 (fr) * 2013-05-03 2014-11-06 Dana Limited Transmission à variation continue à passage de rapport synchrone à double mode
WO2014179719A1 (fr) * 2013-05-03 2014-11-06 Dana Limited Transmission épicycloïdale à variation continue d'entraînement de roue arrière à 4 modes
WO2014186732A1 (fr) * 2013-05-17 2014-11-20 Dana Limited Transmission planétaire à variation continue et à traction avant trimodale à trains d'engrenage empilés
WO2014197711A1 (fr) * 2013-06-06 2014-12-11 Dana Limited Transmission planétaire à variation continue d'entraînement des roues avant et des roues arrière en 3 modes

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2929592B2 (ja) * 1987-12-24 1999-08-03 日本精工株式会社 トロイダル形無段変速装置
JP2003056648A (ja) * 2001-08-10 2003-02-26 Honda Motor Co Ltd 無段変速機用ベルト
JP3832424B2 (ja) * 2002-11-28 2006-10-11 日本精工株式会社 無段変速装置
CN103939602B (zh) * 2007-11-16 2016-12-07 福博科知识产权有限责任公司 用于变速传动装置的控制器
CN101225876A (zh) * 2008-02-20 2008-07-23 陈茂盛 双矩作用轮系的方法及其装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140194242A1 (en) * 2012-09-07 2014-07-10 Dana Limited Ball type cvt/ivt including planetary gear sets
WO2014179717A1 (fr) * 2013-05-03 2014-11-06 Dana Limited Transmission à variation continue à passage de rapport synchrone à double mode
WO2014179719A1 (fr) * 2013-05-03 2014-11-06 Dana Limited Transmission épicycloïdale à variation continue d'entraînement de roue arrière à 4 modes
WO2014186732A1 (fr) * 2013-05-17 2014-11-20 Dana Limited Transmission planétaire à variation continue et à traction avant trimodale à trains d'engrenage empilés
WO2014197711A1 (fr) * 2013-06-06 2014-12-11 Dana Limited Transmission planétaire à variation continue d'entraînement des roues avant et des roues arrière en 3 modes

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
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
US9689477B2 (en) 2012-09-07 2017-06-27 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
US10006527B2 (en) 2012-09-07 2018-06-26 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously 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
US9689482B2 (en) 2013-03-14 2017-06-27 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
US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
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
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
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission
WO2019036324A1 (fr) * 2017-08-14 2019-02-21 Dana Limited Groupes motopropulseurs comportant une transmission à variation continue de type à billes et un train planétaire de ravigneaux

Also Published As

Publication number Publication date
JP2017537285A (ja) 2017-12-14
CN107110303A (zh) 2017-08-29

Similar Documents

Publication Publication Date Title
US9777815B2 (en) 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
WO2016094254A1 (fr) Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes
US20170284508A1 (en) Planetary Powertrain Configuration with a Ball Variator Continuously Variable Transmission Used as a Powersplit
WO2014186732A1 (fr) Transmission planétaire à variation continue et à traction avant trimodale à trains d'engrenage empilés
US10006529B2 (en) Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission
US20170152928A1 (en) 4-mode powersplit transmission based on continuously variable planetary technology
US20180119786A1 (en) Continuously Variable Transmission Having A Ball-Type Continuously Variable Transmission
WO2014179719A1 (fr) Transmission épicycloïdale à variation continue d'entraînement de roue arrière à 4 modes
WO2014179717A1 (fr) Transmission à variation continue à passage de rapport synchrone à double mode
US20190323582A1 (en) Idler assembly for a ball variator continuously variable transmission
WO2016178913A1 (fr) Schéma de puissance avec satellite d'interconnexion pour applications concentriques/coaxiales
US20170248213A1 (en) Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20180119811A1 (en) Ball Variator Continuously Variable Transmission
US20180119810A1 (en) Symmetric Infinitely Variable Transmission Having A Ball-Type 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
US20180372199A1 (en) Multi-mode cvp transmission with geared launch and reverse modes
US20180252303A1 (en) Continuously Variable Drive Having A Ball-Type Continuously Variable Transmission
US20180135734A1 (en) Electromagnetic Device For Ball-Type Continuously Variable Transmission
US20190154125A1 (en) Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20190078668A1 (en) Powersplit Powertrains Having Dual Ball-Type Continuously Variable Transmission
US20180119785A1 (en) Power Converter Having A Ball-Type Continuously Variable Transmission
US20190275884A1 (en) Electric axle with variable ratio, a high efficiency lock up ratio, a neutral
US20170122418A1 (en) Four mode powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20180202550A1 (en) Planetary Powertrain Configurations With A Ball Variator Continuously Variable Transmission Used As A Powersplit
US20180128357A1 (en) Articulating Sub-Housing For A Ball-Type Continuously Variable Planetary Transmission

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: 15868503

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017530122

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15868503

Country of ref document: EP

Kind code of ref document: A1