WO2003001084A1 - Poulie anti-glissement - Google Patents

Poulie anti-glissement Download PDF

Info

Publication number
WO2003001084A1
WO2003001084A1 PCT/GB2002/002876 GB0202876W WO03001084A1 WO 2003001084 A1 WO2003001084 A1 WO 2003001084A1 GB 0202876 W GB0202876 W GB 0202876W WO 03001084 A1 WO03001084 A1 WO 03001084A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
drive system
belt
pressure
retractable members
Prior art date
Application number
PCT/GB2002/002876
Other languages
English (en)
Inventor
John Philip Roger Hammerbeck
Original Assignee
John Philip Roger Hammerbeck
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 John Philip Roger Hammerbeck filed Critical John Philip Roger Hammerbeck
Publication of WO2003001084A1 publication Critical patent/WO2003001084A1/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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/171—Toothed belt pulleys
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H55/38—Means or measures for increasing adhesion
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1263—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially straight path
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
    • F16H7/023—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts with belts having a toothed contact surface or regularly spaced bosses or hollows for slipless or nearly slipless meshing with complementary profiled contact surface of a pulley

Definitions

  • the present invention relates to a non-slip pulley.
  • Pulley and belt systems for rotary power transmission are widely used in industry. It is known disadvantage of pulley and belt systems that they are liable to slip under high torque. This is because power is transmitted by friction between the pulley and the belt and higher torques overcome the friction. Also at higher speeds the belt is lifted from the pulley by centrifugal force, so reducing the frictional contact. Such transmission systems are classified as friction drives. Gear systems, which, because of the engagement of teeth, cannot slip are described as positive drives. However, gears are expensive and heavy compared to belt and pulley systems.
  • An object of the present invention to provide an improved belt and pulley drive system.
  • a drive system comprising a pulley, a belt that extends at least partially around the pulley and a plurality of drive means that are selectively actuatable to cause positive driving engagement between the belt and pulley.
  • the plurality of drive means may comprise a plurality of retractable members, each of which is selectively movable between an extended position in which it extends between the pulley and the belt, thereby causing positive engagement between the pulley and the belt, and a retracted position in which it does not.
  • the retractable members may be mounted on the pulley.
  • the belt may have recesses or holes formed therein.
  • the retractable members may be adapted to be held level with the surface of the pulley by pressure of a part of the belt over them and to move into engagement with a recess or hole in the belt if a recess or hole passes over them, thereby to cause positive engagement between the belt and the pulley.
  • the retractable members may be adapted to remain level with or below the surface of the pulley and then selectively actuated to rise into any suitable recess.
  • An actuator may be provided for actuating movement of the retractable members into the recess or hole.
  • the actuator may comprise a resiliently deformable means, such as a spring.
  • the retractable members may comprise magnetic material, in which case the actuator may comprise magnetic means.
  • the retractable members may comprise movable studs.
  • the studs may be movable in passages defined in the pulley.
  • the studs may be automatically movable under the action of gravity or a centrifugal force.
  • the retractable members may be mounted on the belt.
  • the retractable members may be adapted to be held level with the surface of the belt by pressure of a part of the pulley over them or to move into engagement with a recess in the pulley if a recess passes over them.
  • the retractable members may be adapted to remain level with or below the surface of the belt and then selectively actuated to rise into any suitable recess in the pulley.
  • An actuator may be provided for actuating movement of the retractable members into the recess.
  • the actuator may comprise a resiliently deformable means, such as a spring.
  • the retractable members may comprise magnetic material.
  • the actuator may comprise magnetic means.
  • the retractable members may comprise studs.
  • the retractable members may be mounted on a band that is located between the pulley and the belt.
  • the retractable members may be adapted to be held level with the surface of the band by pressure of a part of the belt over them or to move into engagement with a recess in the belt if a recess passes over them.
  • the retractable members may be adapted to remain level with or below the surface of the band and then selectively actuated to rise into any suitable recess in the belt.
  • An actuator may be provided for actuating movement of the retractable members into the recess.
  • the actuator may comprise a resiliently deformable means, such as a spring.
  • the retractable members may comprise magnetic material.
  • the actuator may comprise magnetic means.
  • the retractable members may comprise studs.
  • the pulley may be operable to drive the belt.
  • the belt may be operable to drive the pulley.
  • the belt may be an endless belt.
  • the belt may be a linear belt.
  • Figure 1 is a cross-section through a portion of a drive system
  • Figure 2 is a similar cross section through another drive system
  • Figure 3 is a cross section through yet another drive system that has a pulley and a plurality of retractable studs, which studs are made of a magnetic material;
  • Figure 4 is a cross-section through another drive system
  • Figure 5 is a cross-section through a belt of the drive of Figure 4;
  • Figure 6 is a top view of a portion of the belt of the drive of Figure 5;
  • Figure 7 is an expanded view of the portion marked A on Figure 4.
  • Figure 8 is a partial sectional view of a coil/pulley configuration according to a second aspect of the invention.
  • Figure 9 shows an alternative embodiment to that of Figure 8;
  • Figure 10 shows one manner of achieving the configuration of Figure 8.
  • Figure 11 shows an alternative manner of achieving the configuration of
  • Figure 12 is a partial sectional view of a further aspect of the invention.
  • Figure 13 is an alternative configuration to that of Figure 12.
  • Figure 1 shows a pulley 10 mounted on a shaft 12 by which rotary power may be input or output from the pulley 10.
  • Extending round the pulley 10 is an endless, elastic belt 14 (full belt not shown) that has a plurality of recesses 15 formed in its inner side, ie the side that is in engagement with the pulley 10.
  • the surface 16 of the pulley 10 that engages with the belt 14 may be of any suitable profile. For clarity, the engagement surface 16 is shown as flat.
  • holes 18 are provided through the engagement surface 16 of the pulley 10 . These may be of any suitable size or shape. Extending through each hole 18 is a stud 20 that is sized to fit within the hole 18 in such a way that it can slide between a position in which it is either level with or below the engagement surface 16 of the pulley 10 and a position in which it extends from that surface 16 to engage with one of the recesses 15 in the belt 14. Means are provided (not shown) for retaining the studs 20 in the holes 18.
  • the pulley 10 rotates and drives the belt 14. This causes the belt 14 to move round the engagement surface 16. If the part of the belt 14 directly adjacent a given stud 20 is flat, then the pressure of the belt 14 prevents the stud 20 moving beyond the surface of the pulley, so that that stud remains at a depressed level substantially flush with the surface of the pulley, see studs 26 and 28. In the event that the part of the belt 14 directly adjacent the stud 20 defines a recess 15, the stud 20 is pushed into the recess 15 under the effect of gravity, see studs 30 and 32, thereby providing positive engagement between the pulley 10 and the belt 14.
  • Figure 1 shows a relatively simple arrangement, in which the engagement of the studs 20 with the belt 14 in the region of the recesses 15 is effected by gravity. This necessitates the pulley 10 axis being near horizontal. In addition, it means that any stud 20 not tightly in engagement with the pulley 10 could slip downwards into the hole 18.
  • the arrangement of Figure 1 could, however, be adapted so that rotation of the pulley 10 causes all of the studs 20 to be forced to move outwardly under the action of a centrifugal force. To do this, the weight of the studs 20 and the speed of rotation of the pulley 10 would have to be taken into account.
  • Figure 2 shows an example of a drive that uses centrifugal force to cause the studs 20 to move into recesses 15 in the belt 14.
  • rotation of the pulley 10 generates a centrifugal force that is sufficient to cause the studs 20 to be pushed outwardly.
  • the part of the belt 14 directly adjacent a given stud 20 is flat, then the pressure of the belt 14 prevents the stud 20 moving beyond the surface 16 of the pulley 10, so that that stud 20 remains at a depressed level substantially flush with the surface 16 of the pulley 10, see studs 34 and 36.
  • rotation of the pulley 10 causes the stud 20 to be pushed into the recess 15.
  • Figure 2 shows a snap shot of a rotating pulley 10, in which all of the studs 20 that are adjacent a recess 15 are forced into it under the action of the centrifugal force.
  • Continued rotation causes each stud 20 that is located in one of the recesses 15 to positively drive the belt 14 round part of its path and thereby avoid slipping. Further rotation causes the studs 20 that are located in the recesses 15 to be moved out of engagement therewith as the belt 14 moves off the pulley 10.
  • the arrangement of the holes and studs 18 and 20 respectively on the pulley 10 can be considerably varied in spacing both round the circumference of the engagement face 16 of the pulley 10 and across the width of the engagement face 16. This is advantageous for reducing wear.
  • the studs 20 could be mounted on the pulley 10, but located at the side of the engagement surface.
  • the belt 14 is provided with suitable recesses or holes 15 large enough to accommodate the studs 20 when they rise. These recesses or holes 15 may be reinforced sufficiently to handle high forces, transmitted when the studs 20 are engaged.
  • the system be capable of slipping to provide a slipping clutch mechanism on starting or as a safety release to reduce torque if the belt is in danger of being overstretched or broken.
  • studs 20 may include magnetic material they may be drawn into the extended position by a permanent magnet 37 mounted at any suitable place round the pulley 10, preferably close to the unengaged face of the pulley 10 to enable the use of the smallest suitable magnet, as shown in Figure 3.
  • studs 20 may also be drawn into engagement by magnets within the belt 14.
  • the studs 20 may also be spring mounted on coil leaf or other springs or resilient material or fluid, so that their natural state is selectively raised or depressed.
  • Mechanical, magnetic, electromagnetic or other suitable means may be employed to change and control the state of the studs 20. Means of controlling the studs may be within the pulley or external.
  • Figure 4 shows another pulley and belt system that has retractable members that can be selectively used to provide a positive drive mechanism between a pulley 10 and an endless, elastic belt 14.
  • each of the belt 14 and the pulley 10 are provided with recesses and a band 38 is provided between them.
  • the band 38 is adapted to transmitted movement of the pulley 10 to the belt 14 or vice versa.
  • Figures 5 and 6 show expanded views of the band 38 of Figure 4. It should be noted, however, that the band 38 could alternatively be fixed directly to the pulley 10. In this case, only the belt 14 would need recesses.
  • leaf spring flaps 40 Formed on both sides of the band 38 are retractable leaf spring flaps 40 that are adapted to act as studs to engage in the recesses 42, 44 formed in either of the belt 14 or the pulley 10.
  • the leaf springs 40 may be formed by stamping out flaps in a length of suitable material, which material should be resiliently deformable.
  • the recesses 42 and 44 on the pulley and belt 10 and 14 respectively and the flaps 40 on the band 38 are shaped to as to prevent slippage between the various parts in the direction of travel of the pulley 10, as shown in Figure 7.
  • the flap 40 is able to expand into the belt recess 44. It should be noted that when the leaf spring flaps 40 are received in recesses 44 in the belt 14, this tends to tension the belt 14, as well as prevent slip thereof. Continued rotation of the pulley causes the band 38 to be positively driven round its path by engagement of the flaps 40 with the pulley 10. Rotation of the band 38 in this way in turn causes the belt 14 to be positively driven round its path by engagement of the flaps 40 in the recesses 44. As before, because the flaps 40 can be maintained in a substantially retracted position and are only selectively extendable into recesses in the belt 14, this means that variations in the spacing of the recesses formed in the elastic belt 14 do not cause problems.
  • An advantage of using a band that engages with both the pulley and the belt is that it provides over-run protection.
  • FIGS 1 to 7 are described above with reference to a drive in which the shaft 12 is used to input power.
  • shaft 12 could equally be used to output rotary power.
  • the belt 14 would be driven so as to cause rotation of the pulley 10 and so shaft 12. It will be understood that operation of the selectively actuatable drive means for causing positive engagement between the belt and the pulley is, however, the same.
  • Figures 1 to 7 show drives in which the belt is a generally flat band, it will be appreciated that the belt could be a coil spring. In this case, instead of selectively moving retractable members into engagement with recesses on a belt, the retractable members would merely be movable into spaces between windings of the spring.
  • This invention is advantageous over conventional belt and pulley friction drives in that it is non-slip and so can handle higher torques. In addition, it is more efficient because it does not have the friction losses caused by belt creep in conventional systems. It is also very suitable for use with elastic belts and coil spring belts employed in continuously variable transmissions of the periodic belt type, such as described in WO 00/19125. This invention is advantageous over gear systems on account of low cost and lightweight.
  • Figures 1 to 7 show a drive in which the belt is endless, it will be appreciated that the pulleys could be used to drive a non-endless belt, in a manner similar to a rack and pinion arrangement.
  • the coil (50) engages the pulley channel (52) of the drive for the (54).
  • a further pressure pulley (56) is urged or biased towards the drive pulley (54) and effectively jams the coil (50) into the drive pulley channel (52). This increases the contact force and is found to reduce slippage accordingly.
  • FIG. 9 An alternative to the "four-point" contact configuration of Figure 8 is shown in Figure 9 in which a pressure wheel (58) again drives the coil into the pulley channel (52).
  • the positioning of the pressure pulley or wheel is preferably at 90° on the drive pulley where the coil disengages the drive pulley at 270°. It would be appreciated that variation of a few degrees in this position either side of the 90° position alters performance of the system and potentially enhances it. It is found that the efficiency of the system shown in Figures 8 and 9 can be up to 90 per cent.
  • the pressure pulley can be either fixedly mounted relative to the drive pulley or it can be movably mounted so as to provide variable pressure and hence a clutch mechanism.
  • the pressure pulley (56) may be slidable along guide (60) in a direction generally tangential to the drive pulley but with a radial component. As a result sliding motion of the pulley (56) will increase or decrease the pressure on the coil (50) as appropriate.
  • FIG 11 shows an alternative system.
  • the pressure pulley (56) is connected by a pivoting arm (62) to a tensioning pulley (64) which tensions the coil (50) upstream of the drive pulley (54).
  • the arm (52) pivots around a fulcrum (66).
  • the tensioning pulley (64) is driven outwardly driving the pressure pulley (56) inwardly hence increasing the force on the coil and reducing slippage.
  • the drive pulley (54) (which is shown in simplified form with the coil (50) lying on the axle) includes a fixed disk or shoulder (70) and a floating disk or shoulder (72).
  • the floating shoulder (72) is inclined inwardly towards the fixed shoulder (70) so as to jam the coil (50) into the drive side of the pulley.
  • the floating shoulder (72) is mounted on a hemispherical shoulder pivot (74) allowing it to maintain its jamming position as the pulley rotates about axle (76).
  • a wedge-like moveable wheel (78) is forced into the non-drive side of the pulley (54).
  • the moveable wheel (78) is in fact spherical and rotates about an axis (80) parallel to the pulley axis (76).
  • the moveable wheel is moveable in the sense that it can be forced towards or away from the pulley axis hence controlling the angle of the floating shoulder and consequently the pressure on the coil (50) once again providing a means for increasing or decreasing the pressure and so providing a clutch mechanism.
  • the movable wheel can be of different profiles, for example having curved or conical side walls.
  • a pair of floating shoulders (72a, 72b) are provided rather than a fixed and floating shoulder.
  • moveable wheel (78) controls the degree of compression of the floating shoulder (72a, 72b).
  • a plurality of ridges (82) can be provided projecting inwardly from the floating shoulders to provide the necessary contact points.
  • the inner faces of the floating shoulders (72a, 72b) can be curved inwardly to the same effect.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

Cette invention se rapporte à une poulie anti-glissement, qui comprend une roue de poulie (10) montée sur un axe (12) et une courroie (14) s'étendant autour de la roue. La courroie peut comporter des encoches (15) dans lesquelles viennent s'engager des tenons (26), afin de réduire le glissement de la courroie (14) sur la roue (10) de la poulie. Les tenons (26) peuvent se déployer sous l'effet de la gravité, par force centrifuge ou sous l'action de tout autre moyen approprié.
PCT/GB2002/002876 2001-06-25 2002-06-25 Poulie anti-glissement WO2003001084A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0115486.3 2001-06-25
GB0115486A GB0115486D0 (en) 2001-06-25 2001-06-25 A non-slip pulley

Publications (1)

Publication Number Publication Date
WO2003001084A1 true WO2003001084A1 (fr) 2003-01-03

Family

ID=9917303

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2002/002876 WO2003001084A1 (fr) 2001-06-25 2002-06-25 Poulie anti-glissement

Country Status (2)

Country Link
GB (1) GB0115486D0 (fr)
WO (1) WO2003001084A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010014269A (ja) * 2008-03-26 2010-01-21 Nissan Motor Co Ltd 無段変速装置
JP2014185752A (ja) * 2013-03-25 2014-10-02 Jatco Ltd 無段変速機および制御方法
WO2014157085A1 (fr) * 2013-03-25 2014-10-02 ジヤトコ株式会社 Transmission à variation continue et procédé de commande
JP2014185718A (ja) * 2013-03-25 2014-10-02 Jatco Ltd 無段変速機および制御方法

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE203266C (fr) *
DE93354C (fr) *
FR1233009A (fr) * 1959-04-27 1960-10-12 Perfectionnements aux poulies de renvoi pour câbles et analogues
GB885427A (en) * 1960-06-14 1961-12-28 Edric Raymond Brooke Improvements relating to belt transmissions
FR1387489A (fr) * 1964-02-14 1965-01-29 Mécanisme de transmission d'un mouvement rotatif pour des moteurs à combustion interne
US3714839A (en) * 1971-03-30 1973-02-06 T Watson Pulley with belt clamping means
US3965767A (en) * 1972-12-01 1976-06-29 Johannes Augustus Rinio Driving pulley mechanism
JPS57127150A (en) * 1981-01-28 1982-08-07 Nitta Kk Belt transmission
EP0599312A1 (fr) * 1992-11-27 1994-06-01 Erich Dr.h.c. Döring Transmission à courroie pour commande de porte
US5638756A (en) * 1993-07-16 1997-06-17 Nihon Biso Co., Ltd. Rope traction device
WO2000019125A1 (fr) 1998-09-25 2000-04-06 John Philip Roger Hammerbeck Variateur de vitesse
WO2000053956A1 (fr) * 1999-03-10 2000-09-14 Zelic Marko Treuil universel automatique traversant

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE203266C (fr) *
DE93354C (fr) *
FR1233009A (fr) * 1959-04-27 1960-10-12 Perfectionnements aux poulies de renvoi pour câbles et analogues
GB885427A (en) * 1960-06-14 1961-12-28 Edric Raymond Brooke Improvements relating to belt transmissions
FR1387489A (fr) * 1964-02-14 1965-01-29 Mécanisme de transmission d'un mouvement rotatif pour des moteurs à combustion interne
US3714839A (en) * 1971-03-30 1973-02-06 T Watson Pulley with belt clamping means
US3965767A (en) * 1972-12-01 1976-06-29 Johannes Augustus Rinio Driving pulley mechanism
JPS57127150A (en) * 1981-01-28 1982-08-07 Nitta Kk Belt transmission
EP0599312A1 (fr) * 1992-11-27 1994-06-01 Erich Dr.h.c. Döring Transmission à courroie pour commande de porte
US5638756A (en) * 1993-07-16 1997-06-17 Nihon Biso Co., Ltd. Rope traction device
WO2000019125A1 (fr) 1998-09-25 2000-04-06 John Philip Roger Hammerbeck Variateur de vitesse
WO2000053956A1 (fr) * 1999-03-10 2000-09-14 Zelic Marko Treuil universel automatique traversant

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 006, no. 224 (M - 170) 9 November 1982 (1982-11-09) *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010014269A (ja) * 2008-03-26 2010-01-21 Nissan Motor Co Ltd 無段変速装置
EP2256370A1 (fr) * 2008-03-26 2010-12-01 Nissan Motor Co., Ltd. Transmission à variation continue
CN101981348A (zh) * 2008-03-26 2011-02-23 日产自动车株式会社 无级变速器
EP2256370A4 (fr) * 2008-03-26 2011-03-09 Nissan Motor Transmission à variation continue
US8506433B2 (en) 2008-03-26 2013-08-13 Nissan Motor Co., Ltd. Continuously variable transmission
JP2014185752A (ja) * 2013-03-25 2014-10-02 Jatco Ltd 無段変速機および制御方法
WO2014157085A1 (fr) * 2013-03-25 2014-10-02 ジヤトコ株式会社 Transmission à variation continue et procédé de commande
JP2014185716A (ja) * 2013-03-25 2014-10-02 Jatco Ltd 無段変速機および制御方法
JP2014185718A (ja) * 2013-03-25 2014-10-02 Jatco Ltd 無段変速機および制御方法
WO2014157002A1 (fr) * 2013-03-25 2014-10-02 ジヤトコ株式会社 Transmission à variation continue et procédé de commande
WO2014157083A1 (fr) * 2013-03-25 2014-10-02 ジヤトコ株式会社 Transmission à variation continue et procédé de commande
CN105074294A (zh) * 2013-03-25 2015-11-18 加特可株式会社 无级变速器及控制方法
CN105074294B (zh) * 2013-03-25 2017-03-15 加特可株式会社 无级变速器及控制方法

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Publication number Publication date
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