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
• • 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
• • 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 transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft
  • F16H2037/0886—Power-split transmissions 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

• the present invention relates to continuously variable ratio transmission systems. It is known to provide a continuously variable ratio transmission system having system input and output shafts and a continuously variable ratio transmission unit (known as a variator) connected to the system input shaft and having a variator output shaft. A mixing epicyclic gear train receives drive from the system input and from the variator input. By appropriate use of clutches or other braking elements, the system can operate in a high-gearing regime or a low- gearing regime. Examples of such transmissions, which disclose arrangements having coaxial system input and output shafts, can be found in JP-A-6-174033 and JP-A-62-255655.
• the first planet gear provides the input for a second epicyclic gear train having an output which is selectively connectable to the system output shaft via a braking element.
• the variator is the lowest efficiency component of the transmission but it enables engine optimisation by ratio matching, resulting in improved overall economy. However, this is not possible at maximum power since this occurs only at one engine speed. If power loss is important, it may be beneficial to sacrifice variable ratio for best efficiency by removing the influence of the variator and operating it at a fixed ratio. The overall result is to potentially avoid a slight reduction in the top speed of the vehicle to which the transmission is fitted.
• a multi-regime, continuously variable ratio transmission system comprising: a system input shaft and a system output shaft; a continuously variable ratio transmission unit (variator) connected to the system input shaft and having a variator output shaft; an output from the variator which is selectively connectable to the system output shaft via a first clutch; a mixing epicyclic gear train having inputs drivably connected to the variator output shaft and the system input shaft and having an output which is selectively connectable to the system output shaft via a first braking element; and a second braking element adapted to lock the output of the mixing epicyclic gear train in a stationary position.
• the system input shaft, the system output shaft and the variator are arranged coaxially with each other and with a second epicyclic gear train comprising a second input sun gear driven by the output of the mixing epicyclic gear train and wherein the second braking element is adapted to selectively lock the input sun gear of the second epicyclic gear train in a stationary position.
• the transmission system comprises intermediate gearing connecting the mixing epicyclic gear train and the input sun gear of the second epicyclic gear train.
• the second epicyclic gear train comprises a second sun gear engaged with a planet gear.
• the sun gear is held stationary with respect to the transmission casing and the first braking element comprises clutch means for selectively connecting the output of the second epicyclic gear train to the system output shaft.
• a method of operating a transmission system as claimed in any of the preceding claims comprises: detecting a condition in which the output from the variator is connected to the system output shaft via the first clutch and in which the mixing epicyclic gear train output is substantially stationary; and applying the second braking element to lock the output of the mixing epicyclic gear train in the stationary position.
• an infinitely variable ratio transmission system comprises a transmission input shaft I and a transmission output shaft O, Connected between the system input shaft I and the system output shaft O is a variator V, preferably of the known toroidal race roller traction type, and a high regime clutch H.
• the transmission input shaft I and the output of the variator V are also connected to a mixing epicyclic gear set E, the output of which is selectively connectable to the transmission output shaft O by means of a low regime clutch L.
• the output of the epicyclic gear set E can also be locked to the transmission casing 40 by means of a further braking element in the form of clutch B.
• One feature of the output of the mixing epicyclic gear set E is that at a certain variator ratio the output of the epicyclic gear set E is stationary (a condition which, when the transmission is in low regime, is l ⁇ iown in the art as "geared neutral").
• the general principle of the present invention is that, with the high regime clutch H engaged and the low regime clutch L disengaged (i.e. with the transmission in high regime) the output of the epicyclic gear set E is continuously sensed and, when the output of the epicyclic gear set E is zero (or close to zero) the additional clutch B is engaged, which locks the output of the epicyclic gear set at zero rotation. Locking clutch B prevents the variator from moving away from the ratio which would result in geared neutral if the low- regime clutch were engaged.
• a continuously variable ratio transmission system comprises a variator V of the l ⁇ iown toroidal race rolling traction type having two toroidally-recessed discs 10 arranged one at each end of the unit and a pair of similar output discs 12, each facing a respective one of the input discs 10 and rotating with each other.
• Sets of rollers 14 are mounted between the opposing faces of the input and output discs 10, 12 to transmit drive from the input discs 10 to the output discs 12 with a ratio which is variable by tilting the rollers 14.
• the input discs 10 are connected to and driven by a system input shaft 16.
• the variator provides an output via a tubular variator output shaft 18 which is arranged coaxially with the input shaft 16.
• the end of the shaft 18 remote from the variator V drives the sun gear SI of a first, mixing epicyclic gear train El.
• the carrier Cl of the gear train El is connected to, and driven by, the input shaft 16 and is also connected to the inner of the two variator input discs 10.
• the carrier Cl carries input planet gears PI which engage with, and are driven by, the sun gear SI.
• the planet gears PI are each mounted on the carrier Cl by means of an associated shaft 20 which additionally carries first and second output planet gears PX1 and PY1.
• Output planet gear PX1 is identical to planet gear PI and transfers the summed output of the gear train El via an output sun gear S2 (of the same size as input sun gear SI) to an intennediate output shaft 22 arranged coaxially with the system input shaft 16.
• Drive from the intermediate output shaft can be selectively transmitted via a high-regime clutch H to a system output shaft 24.
• Output planet gear PY1 is of smaller diameter than planet gears PI and PX1 and meshes with a pinion 26 formed on one end of a tubular intermediate output shaft 28 arranged coaxially with the input shaft 16.
• the opposite end of the intermediate output shaft is also provided with a pinion 30 of smaller diameter than pinion 26.
• the pinion 30 meshes with larger diameter planet gears P2 of a second, simple reversing epicyclic gear set D2.
• the planet gears P2 are mounted on a carrier C2 which is connected to a second tubular intermediate output shaft 32 arranged coaxially with the system input shaft 16, and which in turn is connected to the system output shaft 24.
• the planet gears P2 of the second epicyclic gear set E2 are each located at one end of a respective shaft 34 mounted in the carrier C2.
• the opposite end of each shaft 34 carries a further, smaller planet gear PX2 which mesh with a sun gear 36 which is fixedly connected to the transmission casing 40.
• the transmission can operate in one of three regimes, namely high regime, low regime and synchronous mode. In high regime, the high regime clutch H is engaged and the low regime clutch L is disengaged.
• the tubular intermediate output shaft 28 i.e. the second output of the mixing epicyclic gearset El
• the present invention takes advantage of this situation by detecting a geared neutral condition and applying the clutch B to lock the intermediate output shaft 28 to the transmission casing 40 in the condition in which the output of a second mixing epicyclic gear train formed by gears SI, PI, PY1 and 26 and carrier Cl is stationary. The effect of this is to effectively lock the variator in a fixed ratio corresponding to geared neutral. Power is then transmitted from input shaft 16 at fixed ratio via a first mixing epicyclic gear train formed by carrier Cl and the pairs of gears S2/PX1 and 26/PY1.
• the high regime clutch H In low regime, the high regime clutch H is disengaged and the low regime clutch L is engaged. Disengagement of the high regime clutch H isolates the system output shaft 24 from the output planet gear PX1 of the mixing epicyclic gear set El. Furthermore, engagement of the low regime clutch L allows the output drive from the first mixing epicyclic gear set El to the second epicyclic gear set E2 to be transferred to the carrier C2 of the second epicyclic gear set E2 by providing a reaction force from the transmission casing 40. The drive is then fransmitted to the second tubular intermediate output shaft 32 and thence to the system output shaft 24.
• Moving from high regime to low regime or vice versa can be achieved in so-called "synchronous mode" in which the transmission operates in a condition in which the mtermediate output shaft 22 leading from the mixing epicyclic gear set El and the second tubular intermediate output shaft 32 leading from the second epicyclic gear set E2 rotate at (or very near) the same speed.
• the clutch of the new regime is engaged, whereby both clutches are simultaneously engaged for a short time and the clutch of the old regime is then disengaged.
• the present invention allows the use of a mixing epicyclic gear set El which does not have an annulus or ring gear. Not only does this reduce the weight of the transmission, but it also allows greater flexibility with the selection of the relative sizes of planetary gears PI, PX1 and PY1. This in turn allows the speed of the components to be reduced and reduces the number of meshes to a mirumum.
• the invention is not restricted to the details of the foregoing embodiment.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Transmission Devices (AREA)
• Vehicle Body Suspensions (AREA)
• Structure Of Transmissions (AREA)
• Eye Examination Apparatus (AREA)
• Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
• Transmissions By Endless Flexible Members (AREA)
• Control Of Transmission Device (AREA)

Priority Applications (7)

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

Country Status (13)

Cited By (2)

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Citations (3)

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• 2003
  • 2003-07-01 GB GBGB0315408.5A patent/GB0315408D0/en not_active Ceased
• 2004
  • 2004-07-01 WO PCT/GB2004/002841 patent/WO2005003597A1/en not_active Ceased
  • 2004-07-01 CN CN200480018840A patent/CN100582528C/zh not_active Expired - Fee Related
  • 2004-07-01 BR BRPI0411997-5A patent/BRPI0411997A/pt not_active IP Right Cessation
  • 2004-07-01 CA CA002529885A patent/CA2529885A1/en not_active Abandoned
  • 2004-07-01 DE DE602004016997T patent/DE602004016997D1/de not_active Expired - Lifetime
  • 2004-07-01 RU RU2006101863/11A patent/RU2338938C2/ru not_active IP Right Cessation
  • 2004-07-01 AT AT04743188T patent/ATE410622T1/de not_active IP Right Cessation
  • 2004-07-01 JP JP2006516488A patent/JP2007516385A/ja active Pending
  • 2004-07-01 MX MXPA05014097A patent/MXPA05014097A/es active IP Right Grant
  • 2004-07-01 US US10/561,727 patent/US7530916B2/en not_active Expired - Lifetime
  • 2004-07-01 EP EP04743188A patent/EP1639273B1/en not_active Expired - Lifetime
  • 2004-07-01 KR KR1020057025444A patent/KR20060034251A/ko not_active Ceased

Patent Citations (3)

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