WO2014039440A1 - Transmission à variation continue basée sur un planétaire à variation continue du type à bille comprenant des trajectoires de division de puissance par l'intermédiaire d'un pignon conique - Google Patents

Transmission à variation continue basée sur un planétaire à variation continue du type à bille comprenant des trajectoires de division de puissance par l'intermédiaire d'un pignon conique Download PDF

Info

Publication number
WO2014039440A1
WO2014039440A1 PCT/US2013/057839 US2013057839W WO2014039440A1 WO 2014039440 A1 WO2014039440 A1 WO 2014039440A1 US 2013057839 W US2013057839 W US 2013057839W WO 2014039440 A1 WO2014039440 A1 WO 2014039440A1
Authority
WO
WIPO (PCT)
Prior art keywords
variator
variable transmission
vehicle
bevel gear
ring assembly
Prior art date
Application number
PCT/US2013/057839
Other languages
English (en)
Inventor
James F. Ziech
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 WO2014039440A1 publication Critical patent/WO2014039440A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • 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
    • F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • 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
    • 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
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • 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
    • F16H2037/0893—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 characterised in the ratio of the continuously variable transmission is different from zero when the output shaft speed is zero

Definitions

  • CVTs Continuously Variable Transmissions or CVTs
  • Those CVTs are of 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 can also shift to the most optimum ratio providing more power.
  • a CVT can 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 transmission by disengaging to shift from one discrete ratio to engage the next ratio.
  • variable transmission comprising: an input shaft; a bevel gear power divider drivingly engaged with the input shaft, and comprising a first bevel gear drivingly engaged with a variator input shaft, and a second bevel gear drivingly engaged with an output shaft; and a variator comprising, a variator carrier assembly, a first ring assembly, and a second ring assembly; and the output shaft.
  • the variable transmissions described herein may be used in any vehicle type requiring such functions provided by these variable transmission.
  • the bevel gear power divider unit splits ingoing torque 50/50 between the variator and the output shaft.
  • the bevel gear power divider unit splits ingoing torque 10/90 (variator/output), 20/80, 25/75, 30/70, 40/60, 60/40, 70/30, 75/25, 80/20, or 90/10 between the variator and the output shaft.
  • the variator comprises a continuously variable variator, an infinitely variable variator, or a combination thereof.
  • the input shaft has a gear at an end thereof that engages with a plurality of bevels of the bevel gear power divider unit.
  • variator balls of the variator carrier assembly, the first ring assembly, and the second ring assembly are rotatably disposed in the housing.
  • variable transmission further comprises a gearbox drivingly engaged with the output shaft.
  • the gearbox is a two speed gearbox.
  • the gearbox is configured to compensate for spread loss caused by the bevel gear power divider unit.
  • the gearbox is configured to allow for a reverse drive mode.
  • the variable transmission configured to change continuously its ratio to provide the best ratio achievable for an engine engaged thereto in function of the objectives of consumption or power.
  • the input shaft and the output shaft are at least partially disposed in the housing.
  • variable transmission comprises an axial force generator configured to generate sufficient axial force to properly operate the vehicle transmission.
  • the axial force generator comprises one or more clamping mechanisms.
  • the axial force generator comprises a ball ramp.
  • the axial force generator comprises a ball ramp thrust ring.
  • the axial force generator comprises a load applied during assembly of the variable transmission.
  • the input shaft is drivingly engaged with a torsional dampener disposed between an engine and the variable transmission.
  • the first ring assembly is rotatably disposed in the housing drivingly engaged with the bevel gear power divider unit, the first ring assembly comprising a first variator ball engagement surface that is in driving engagement with a plurality of variator balls of the carrier assembly. In some embodiments, the first ring assembly is rotatably disposed in the housing drivingly engaged with the bevel gear power divider unit using the variator input shaft.
  • a first variator ball engagement surface is formed in an input ring of the first ring assembly. In some embodiments, a first variator ball engagement surface is formed in a distal end of the first ring assembly. In some embodiments, the first variator ball engagement surface is a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls. In some embodiments, the first variator ball engagement surface is in driving engagement with each of the variator balls of the carrier assembly through one of a boundary layer type friction and an
  • a carrier assembly is rotatably disposed in the housing and is drivingly engaged first ring assembly, the carrier assembly comprising an annular
  • each of the ball axle shafts is adjusted using a cam style tilting mechanism.
  • each of the ball axle shafts is adjusted using a split carrier axle skewing mechanism.
  • the second ring assembly is rotatably disposed in the housing, and wherein the second ring assembly comprises and a second variator ball engagement surface that is in driving engagement with variator balls of the carrier assembly.
  • the second variator ball engagement surface is formed in a distal end of the second ring assembly.
  • a second variator ball engagement surface is formed in an input ring of the first ring assembly.
  • the second variator ball engagement surface is a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls.
  • the second variator ball engagement surface is in driving engagement with each of the variator balls of the first carrier assembly through one of a boundary layer type friction and an elastohydrodynamic film.
  • the output shaft is drivingly engaged with a vehicle output.
  • a vehicle driveline comprising: an engine; a dampener in driving engagement with the engine; a variable transmission as described herein or obvious to one of skill in the art upon reading the disclosure herein, and a vehicle output.
  • the vehicle driveline may comprise a starting device.
  • the vehicle output comprises a wheel differential and one or more wheels of a vehicle.
  • the vehicle output comprises a wheel differential and a drive axle.
  • the dampener is disposed between the engine and the variable transmission.
  • the dampener comprises at least one torsional spring.
  • the dampener is coupled with a clutch.
  • the starting device is a wet or dry clutch.
  • the vehicle driveline comprises a starting device.
  • the starting device comprises a torque converter.
  • the starting device is in locked mode after startup.
  • FIG 1 depicts certain elements of an embodiment CVP.
  • Figure 2 depicts a ratio change mechanism in an embodiment CVP.
  • Figure 3 depicts a basic driveline configuration including an embodiment CVT.
  • Figure 4 depicts an embodiment CVP variator coupled to a bevel gear power divider unit and an additional gearbox.
  • CVTs Infinite Variable Transmission or IVT. Where the CVT is limited to positive speed ratios, the IVT configuration can perform a neutral gear and even reverse ratios steplessly. A CVT can be used as an IVT in some driveline configurations.
  • IVT Infinite Variable Transmission
  • CVP constant variable planetary
  • This CVT comprises of a certain number of balls 997 (for example, 3-15 balls), depending on the application, two discs 995, 996 or annular rings each having an engagement portion that engages the variator balls as input and output as shown on FIG. 1.
  • the engagement portions may be in a conical or toroidal convex or concave surface contact with the variator balls, as input and output.
  • the CVT may include an idler 999 contacting the balls as well as shown on FIG. 1.
  • the variator balls are mounted on axes 998, themselves held in a cage or carrier allowing changing the ratio by tilting the variator balls' axes.
  • Other types of ball CVTs also exist, like the one produced by Milner but are slightly different. These alternative ball CVTs are additionally contemplated herein.
  • the working principle 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 variator 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.
  • the CVT 103 includes a CVP (continuously variable planetary) and is used to replace traditional transmission and is located between the engine 100 and the differential 102 as shown on FIG. 3.
  • a torsional damper 101 has to be introduced between the engine and the CVT 103 to avoid transferring torque peaks and vibrations that could seriously damage the CVT 103.
  • this damper 101 can be coupled with a clutch for the starting function.
  • FIG. 4 An embodiment CVP is depicted in FIG. 4.
  • This configuration uses a starting device ((like a torque converter or a wet or dry clutch) and a bevel gear power divider unit 2, with which the CVP is connected to.
  • An output shaft 10 is then coupled to the bevel gear power divider unit 2 and goes to an additional gearbox 3 (such as a two speed or forward/reverse gearbox), then to a wheel differential.
  • the bevel gear power divider unit 2 splits the ingoing torque 50/50.
  • One path goes through the variator 1 and the other path is linked with the output (output shaft 10) of the variator 1.
  • the power splitting causes this configuration to have a higher native efficiency and the variator size can be chosen smaller.
  • the central part of that configuration is an embodiment variator.
  • the variator may be of multiple configurations, including a continuously variable variator, or an infinitely variable variator, or a combination thereof in coordination with any combination of planetary gearsets or portions thereof, or in coordination with combinations of one or more clutches (grounding devicees, brakes, or other types of clutches).
  • a first configuration of a vehicle driveline includes a variable transmission 103 as shown in FIG. 4.
  • the variable transmission (CVP) 103 includes a variator 1 that includes a variator carrier assembly 14, a first ring assembly, and a second ring assembly.
  • the variable transmission 103 comprises an input shaft 16 drivingly engaged to a bevel gear power divider unit 2 having a variator input 18 and an output shaft 10 drivingly engaged thereto.
  • the input shaft 16 has a gear 20 formed at an end thereof that engages with a plurality of bevels of the bevel gear power divider unit 2.
  • the input shaft 16 and an output shaft 10 of the variable transmission are at least partially disposed in a housing.
  • Variator balls 18a, 18b of the variator carrier assembly, the first ring assembly, and the second ring assembly are rotatably disposed in the housing.
  • the variable transmission further includes a bevel gear power divider unit 2 and/or a gearbox 3.
  • Ball ramps indicated in FIG. 4 by a circle between a pair of vertical lines, making up a first thrust ring on the first ring assembly and a second thrust ring on the second ring assembly are disposed between components of the variable transmission 103 as shown to generate an amount of axial force necessary for proper operation of the variable transmission 103 (i.e. transfer of torque); however, it is understood that the amount of axial force necessary for proper operation may be generated by a clamping mechanism (not shown) or as a load applied during assembling of the variable transmission 103. As depicted in FIG. 4, a ball ramp on each side of the variator 1 provides the clamping force necessary to transfer the torque in this embodiment.
  • the input shaft 16 has a first end drivingly engaged with the engine, second end drivingly engaged with a bevel gear of the bevel gear power divider unit 2.
  • the bevel gear power divider unit is drivingly engaged with the first ring assembly (of the variator 1).
  • the bevel gear power divider unit 2 is additionally drivingly engages and couples to the output shaft 10 of the CVP.
  • the bevel gear power divider unit 2 splits the torque from the ICE (engine) between the output shaft 10 and the variator first ring assembly.
  • the split is described as being 50/50, in this embodiment, however other torque splits such as 10/90 (Variator/Output), 20/80, 25/75, 30/70, 40/60, 60/40, 70/30, 75/25, 80/20, or 90/10 is contemplated herein.
  • the variator carrier assembly is rotatably disposed in the housing and includes a plurality of ball axle shafts tiltably disposed therein in an annular arrangement.
  • Each of the ball axle shafts includes a variator ball 18a, 18b rotatably disposed thereon.
  • Each of the ball axle shafts may be adjusted using one of a cam style tilting mechanism and a split carrier axle skewing mechanism.
  • the variator carrier assembly is drivingly engaged with first ring assembly.
  • the variator carrier assembly comprises an annular arrangement of the plurality of tiltable variator balls 18a. 18b each having ball axle shafts.
  • the variator carrier assembly is configured to be prevented from rotating relative to the housing by a grounding device 22, in the embodiment of FIG. 4.
  • the first ring assembly is an annular member rotatably disposed in the housing. As mentioned hereinabove, the first ring assembly is drivingly engaged with the input shaft 16 using the bevel gear power divider unit 2.
  • a first variator ball engagement surface 38 is formed in a distal end of the first ring assembly.
  • the first variator ball engagement surface 38 may be a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls 18a, 18b.
  • the first variator ball engagement surface 38 is in driving engagement with each of the variator balls 18a, 18b through one of a boundary layer type friction and an elastohydrodynamic film.
  • the second ring assembly is an annular member rotatably disposed in the housing.
  • the second ring assembly is drivingly engaged with the output shaft 10.
  • the output shaft 10 is additionally coupled to the bevel gear power divider unit 2 which couples to an additional gearbox 3 (such as a two speed gearbox or a forward/reverse gearbox), which then couples to a differential.
  • an additional gearbox 3 such as a two speed gearbox or a forward/reverse gearbox
  • the split is described as being 50/50, in this embodiment, however other torque splits such as 10/90 (Variator/Output), 20/80, 25/75, 30/70, 40/60, 60/40, 70/30, 75/25, 80/20, or 90/10 is contemplated herein.
  • a second variator ball engagement surface 52 is formed in a distal end of the second ring assembly.
  • the second variator ball engagement surface 52 may be a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls 18a, 18b.
  • the second variator ball engagement surface 52 is in driving engagement with each of the variator balls 18a, 18b through one of a boundary layer type friction and an elastohydrodynamic film.
  • the variator is also used in CVP mode by blocking the carrier of the variator. This may be achieved by the grounding device 22 as shown in FIG. 4.
  • the grounding device 22 may be a mechanism that grounds the variator carrier.
  • cam axle tilt reaches into the variator along the central axis of the variator and allows the ratio shifting while the carrier is held stationary from rotation.
  • the skew shifting is accomplished by indexing at a variable angle the two halves of the variator carrier relative to one another through a pair of control levers that are located at the grounding mechanism at the outside of the carrier.
  • This configuration comprises a starting device to provide standstill and very low vehicle speeds, for example up to 10 kph.
  • a torque converter may be used, for non- limiting example, giving damping and torque multiplication.
  • the torque converter may be in lock-up mode to improve efficiency.
  • the bevel gear power divider unit 2 causes the transmission configuration to lose ratio spread. This may be compensated for by adding an additional two speed gearbox 3. Also, driving in reverse is provided by the additional gearbox 3. By adding the additional two speed gearbox 3, spread is similar to a traditional gearbox.
  • This device is able to change continuously its ratio to provide an optimized or optimum ratio achievable for the engine in function of the objectives of fuel consumption or power.
  • a manual or automatic transmission only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift from one ratio to another ratio.
  • the only interruptions of power in this device are the ratios shifting of the additional gearbox.
  • Other advantages of this configuration are that a relatively small variator can be chosen; spread is similar to a traditional gearbox and the native efficiency of the transmission is increased by using the CVP in a powersplit device, therefore letting a part of the power passing through a more efficient mechanical path.

Abstract

L'invention porte sur une transmission à variation, qui comprend un arbre d'entrée ; un diviseur de puissance à engrenages coniques venant en prise d'entraînement avec l'arbre d'entrée, et comprenant un premier engrenage conique venant en prise d'entraînement avec un arbre d'entrée de variateur, et un second engrenage conique venant en prise d'entraînement avec un arbre de sortie ; et un variateur comprenant un ensemble de porteur de variateur, un premier ensemble de couronne et un second ensemble de couronne ; et l'arbre de sortie. L'unité de diviseur de puissance à engrenages coniques divise un couple entrant entre le variateur et l'arbre de sortie qui vient en prise d'entraînement avec la sortie de véhicule.
PCT/US2013/057839 2012-09-07 2013-09-03 Transmission à variation continue basée sur un planétaire à variation continue du type à bille comprenant des trajectoires de division de puissance par l'intermédiaire d'un pignon conique WO2014039440A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201261697953P 2012-09-07 2012-09-07
US61/697,953 2012-09-07
US201361778200P 2013-03-12 2013-03-12
US61/778,200 2013-03-12

Publications (1)

Publication Number Publication Date
WO2014039440A1 true WO2014039440A1 (fr) 2014-03-13

Family

ID=50237555

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2013/057839 WO2014039440A1 (fr) 2012-09-07 2013-09-03 Transmission à variation continue basée sur un planétaire à variation continue du type à bille comprenant des trajectoires de division de puissance par l'intermédiaire d'un pignon conique

Country Status (1)

Country Link
WO (1) WO2014039440A1 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8986150B2 (en) 2012-09-07 2015-03-24 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9052000B2 (en) 2012-09-07 2015-06-09 Dana Limited Ball type CVT/IVT including planetary gear sets
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4784017A (en) * 1986-07-03 1988-11-15 Johnshoy Edward W Continuously variable transmission and torque retaining differential
US20040171452A1 (en) * 2003-02-28 2004-09-02 Miller Donald C. Continuously variable transmission
US20080185201A1 (en) * 2004-12-22 2008-08-07 Timothy Bishop Spring Hybrid Drive
US7717815B2 (en) * 2005-07-23 2010-05-18 Luk Lamellen Und Kupplungsbau Beteiligings Kg Power-branched transmission having a plurality of transmission ration ranges with continuously variable transmission ratio

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4784017A (en) * 1986-07-03 1988-11-15 Johnshoy Edward W Continuously variable transmission and torque retaining differential
US20040171452A1 (en) * 2003-02-28 2004-09-02 Miller Donald C. Continuously variable transmission
US20080185201A1 (en) * 2004-12-22 2008-08-07 Timothy Bishop Spring Hybrid Drive
US7717815B2 (en) * 2005-07-23 2010-05-18 Luk Lamellen Und Kupplungsbau Beteiligings Kg Power-branched transmission having a plurality of transmission ration ranges with continuously variable transmission ratio

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US8986150B2 (en) 2012-09-07 2015-03-24 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US9416858B2 (en) 2012-09-07 2016-08-16 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
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US9052000B2 (en) 2012-09-07 2015-06-09 Dana Limited Ball type CVT/IVT including planetary gear sets
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US10006527B2 (en) 2012-09-07 2018-06-26 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9689477B2 (en) 2012-09-07 2017-06-27 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9644530B2 (en) 2013-02-08 2017-05-09 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9638301B2 (en) 2013-03-14 2017-05-02 Dana Limited Ball type continuously variable transmission
US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9689482B2 (en) 2013-03-14 2017-06-27 Dana Limited Ball type continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission

Similar Documents

Publication Publication Date Title
US10006527B2 (en) Ball type continuously variable transmission/infinitely variable transmission
US10088026B2 (en) Ball type CVT with output coupled powerpaths
US9556943B2 (en) IVT based on a ball-type CVP including powersplit paths
US9353842B2 (en) Ball type CVT with powersplit paths
WO2014039440A1 (fr) Transmission à variation continue basée sur un planétaire à variation continue du type à bille comprenant des trajectoires de division de puissance par l'intermédiaire d'un pignon conique
US9052000B2 (en) Ball type CVT/IVT including planetary gear sets
US9638301B2 (en) Ball type continuously variable transmission
US9638296B2 (en) Ball type CVT including a direct drive mode
US20170152928A1 (en) 4-mode powersplit transmission based on continuously variable planetary technology
WO2014165259A1 (fr) Transmission comprenant un entraînement composite série à variateurs cvt et ivt

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: 13834872

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: 13834872

Country of ref document: EP

Kind code of ref document: A1