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WO1991019118A1 - Transmission variable en continu - Google Patents

Transmission variable en continu Download PDF

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Publication number
WO1991019118A1
WO1991019118A1 PCT/GB1991/000824 GB9100824W WO9119118A1 WO 1991019118 A1 WO1991019118 A1 WO 1991019118A1 GB 9100824 W GB9100824 W GB 9100824W WO 9119118 A1 WO9119118 A1 WO 9119118A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
gear set
transmission system
gear
planetary
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/GB1991/000824
Other languages
English (en)
Inventor
Michael Joseph Egan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BARTON GORDON PAGE
Original Assignee
BARTON GORDON PAGE
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 BARTON GORDON PAGE filed Critical BARTON GORDON PAGE
Publication of WO1991019118A1 publication Critical patent/WO1991019118A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/721—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously the secondary drive being an energy dissipating device, e.g. regulating brake, in order to vary speed continuously
    • F16H3/722—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously the secondary drive being an energy dissipating device, e.g. regulating brake, in order to vary speed continuously the secondary drive being a fluid throttle
    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion

Definitions

  • This invention relates to a rotary transmission system, and in the preferred embodiment of the invention provides a continuously variable transmission suitable for use in a motor vehicle.
  • a rotary transmission system comprising: a first planetary gear set driven by a rotary input shaft; a second planetary gear set driven by the first planetary gear set; a third planetary gear set driven by the second planetary gear set; an output shaft driven by the sun gear of the third planetary gear set; and means for rotating the sun gear of the second planetary gear set to vary the gear ratio of the transmission system.
  • the means for rotating the sun gear of the second planetary gear set comprises means for coupling the sun gear to the output shaft for rotation therewith.
  • the means coupling the sun gear of the second planetary gear set to the output shaft permits relative rotation of the sun gear of the second planetary gear set and the output shaft .
  • the means coupling the sun gear of the second planetary gear set to the output shaft comprises means selectively operable to allow the sun gear of the second planetary gear set to rotate slower than or be driven faster than the output shaft .
  • Such coupling means may be utilized to vary the ratio of the transmission system in response to varying load requirements.
  • auxiliary means are provided for fixing the sun gear of the second planetary gear set in a fixed position whereby the rotary transmission system will provide a fixed low transmission ratio.
  • Figure 1 illustrates schematically in longitudinal cross-section a first embodiment of the invention
  • Figures 2-5 are respectively cross-sectional views on the lines A-A, B-B, C-C, and D-D of Figure 1;
  • Figure 6 is a view corresponding to Figure 1 of a second embodiment of the invention.
  • Figures 7-9 are cross-sectional views on the lines B-B, C-C, and D-D respectively of Figure 6;
  • Figure 10 illustrates a third embodiment of the invention.
  • a continuously variable transmission which may be utilized in a motor vehicle, for example a passenger car.
  • the overall profile of the casing of the CVT is substantially the same as that of an existing gear box assembly and accordingly the illustrated CVT may be used as an alternative to the gear box assembly without changes to the mounting or space provisions of the motor car. It will be appreciated, however, that the exact profile of the casing is not critical and that embodiments of the present invention may be used in a wide range of motor vehicle applications or other uses.
  • the illustrated CVT comprises an oil pump 1 and an input shaft 2 which is driven from a conventional torque convertor to provide a rotary input to the CVT.
  • the input shaft 2 drives a reversing system A which in turn provides an input via coaxial shafts 13 and 14 to a rotary transmission system B .
  • the rotary transmission system drives an output shaft 45 which can be used to drive the driven wheels of a motor vehicle in conventional manner.
  • the input shaft 2 is drivingly connected to the sun gear 3 of a planetary gear set which comprises , in addition to the sun gear 3, a ring gear 5 and a plurality of planetary gears 4 mounted on a planetary gear carrier 6.
  • a selectively operable brake band 7 is provided for preventing rotation of the ring gear 5.
  • a first clutch disc 9 is connected by way of splines to one end of the shaft 14, and a second clutch disc 10 is connected by way of splines to the tubular shaft 13.
  • Hydraulically driven locking pins 12 are provided for selectively locking the clutch disc 9 or the ring gear 5 to the planetary gear carrier 6.
  • locking pins 11 are provided for selectively locking the clutch disc 10 to the planetary gear carrier 6.
  • Locking pins 16 are provided for selectively locking the tubular shaft 13 relative to the CVT housing.
  • the brake band 7 In use, if forward motion is required the brake band 7 is actuated to lock the ring gear relative to the housing.
  • the input shaft 2 is then rotated (for the purposes of illustration in the clockwise direction) by the engine to rotate the sun gear 3.
  • Locking pins 12 are positioned to lock the clutch disc 9 to the planetary gear carrier and locking pins 16 are actuated to lock the tubular shaft 13 relative to the housing. Clockwise rotation of the sun gear 3 will accordingly cause the planetary gear carrier 6 to rotate and this in turn will drive the shaft 14 clockwise via the pins 12. If reverse drive is required the brake 7 is released and the pins 12 are shifted to lock the ring gear 5 to the planetary gear carrier 6.
  • the locking pins 11 are operated to lock the clutch disc 10 to the planetary gear carrier 6 and the locking pins 16 are withdrawn to permit rotation of the tubular shaft 13. Accordingly, with the controls set in this manner clockwise rotation of the input shaft 2 will cause the sun gear 3, planetary gear carrier 6, ring gear 5, clutch disc 10, and tubular shaft 13 to rotate, as a unit in the clockwise direction.
  • the rotary transmission system comprises a clutch disc 17 and three interconnected planetary gear sets for producing rotary drive of the output shaft 45.
  • the first planetary gear set comprises a clutch disc 17 and a sun gear 22 secured to the tubular shaft 13; a plurality of planetary gears 20 mounted on a planetary gear carrier 18 which is secured to the input shaft 14; and a ring gear 21.
  • a brake band 19 is provided for locking the planetary gear carrier 18 relative to the housing of the CVT when required.
  • the second planetary gear set comprises a sun gear 26, a plurality of planetary gears 24 mounted on a planetary gear carrier 25; and a ring gear 44.
  • the third planetary gear set comprises a sun gear 43 secured to the output shaft 45; a plurality of planetary gears 42 mounted on a planetary gear carrier 41 ; and the ring gear 44 which is common to both the second and the third planetary gear sets.
  • the planetary gear carrier 25 of the second planetary gear set is connected by way of a drum 23 to the planetary gear carrier 41 of the third planetary gear set, and is connected to the ring gear 21 of the first planetary gear set. Accordingly, the ring gear 21 of the first planetary gear set and the planetary gear carriers 25 and 41 respectively of the second and third planetary gear sets rotate as a unit .
  • the ring gear 44 which is common to both the second and third planetary gear sets is mounted for free rotation on the hub of the sun gear 43 of the third planetary gear set .
  • the sun gear 26 of the second planetary gear set is coupled to the output shaft 45 by way of a coupling device 28.
  • the coupling device 28 is preferably in the form of a hydraulic fluid pump/motor which displaces hydraulic fluid in response to relative rotation of the sun gear 26 and the output shaft 45. By permitting the pumping device to displace fluid the sun gear 26 may be permitted to rotate more slowly than the output shaft 45 and by progressively throttling the output of hydraulic fluid the speed of rotation of the sun gear 26 may be increased to that of the output shaft 45. By operating the device 28 as a motor the sun gear 26 may be rotated faster than the output shaft 45.
  • a brake 30 is selectively operable to lock the casing of the device 28, and with it the sun gear 26, relative to the casing of the CVT.
  • the reversing system In use, if forward motion is required the reversing system is operated as described above to lock the tubular shaft 13 and to cause clockwise rotation of the shaft 14. Because the shaft 13 is locked, the sun gear 22 will also be locked and rotation of the shaft 14 will cause the planetary gears 20 to run around the sun gear 22 and drive the ring gear 21 in the clockwise direction. This will in turn cause clockwise rotation of the planetary gear carriers 25 and 41. Initially, the sun gear 26 will be stationary and accordingly the rotating planetary gears 24 will drive the ring gear 44 which will in turn cause the sun gear 43 of the third planetary gear set to be driven as a result of the forcible rotation of the planetary gears 42 by the planetary gear carrier 41.
  • the various gear ratios are preferably chosen such that during this initial phase of operation the overall ratio of the CVT is about 5:1.
  • the arrangements may be chosen such that with an initial engine speed of 1000 rpm the CVT provides an overall ratio of 5:1. By the time the engine speed has increased to 2500 rpm the overall ratio has fallen to 1 :1.
  • the overall ratio of the CVT may be varied by varying the rotational speed of the sun gear 26 relative to the output shaft 45. This may be of use in coping with variable torque demands, for example such as may be encountered during hill climbing.
  • the ring gear 26 may be permitted to rotate more slowly than the output shaft 45, thereby reducing the overall ratio of the gear box.
  • the overall ratio may be increased. This may be of particular assistance in providing engine braking under overrun conditions. If the brake 30 is operated the sun gear 26 will be locked relative to the casing and the overall gear ratio of the CVT will remain at the initial level , 5 :1 in the example cited above. Under these conditions there is no restriction to the outlet of the device 28 and the shaft 45 may turn freely within the sun gear 26.
  • FIG. 6-9 a second embodiment of the invention is illustrated.
  • a modified reversing system C is used, and the arrangement of the various elements of the planetary gear sets in the rotary transmission system D is changed.
  • the fundamental operation of the rotary transmission system is substantially as described above with the sun gear of the third planetary gear set driving the output shaft, and the sun gear of the second planetary gear set coupled to the output shaft to vary the overall ratio of the CVT.
  • the input shaft 102 (which as previously is driven from a conventional torque converter) is splined to the sun gear 103 of a planetary gear set .
  • the ring gear 104 of the planetary gear set is fast with the casing of the CVT and the planetary gears 105 are mounted on a planetary gear carrier 106 which, by virtue of the fixed nature of the ring gear 104 is caused to rotate in the same (clockwise) direction as the input shaft 102, when the input shaft is rotated.
  • the planetary gear carrier 106 is secured to a crown wheel 107 for rotation therewith.
  • a second crown wheel 112 is secured by means of a bevel crown gear carrier 111 to an intermediate shaft 138 which constitutes the input shaft to the rotary transmission system D.
  • a brake band 108 is applied to fix, relative to the casing, a bevel gear carrier 109.
  • a plurality of bevel gears 110 are mounted in the bevel gear carrier for rotation about axes extending perpendicular to the axis of the input shaft 102.
  • Each bevel gear 110 is in mesh with the crown wheel 107 and the crown wheel 112. Under these conditions, rotation of the input shaft 102 in the clockwise direction will drive the planetary gear carrier 106 in the clockwise direction as described above, and this will in turn drive the crown wheel in the clockwise direction.
  • the bevel gears 110 will each rotate about their own axes and will as a result drive the crown gear 112, and with it the intermediate shaft 138, in the reverse, (anticlockwise) direction. It will be noted that the reversing system provides the same speed of rotation of the intermediate shaft 138 relative to that of the input shaft 102, regardless of the direction of rotation of the intermediate shaft 138.
  • the shaft 138 is rotationally fast with the ring gear 118 of a first planetary gear set which, in addition to the ring gear 118, includes a sun gear 116 fixed relative to the CVT casing and a plurality of planetary gears 117 mounted on a planetary gear carrier 115.
  • the planetary gear carrier 115 is connected by way of a drive drum 119 to the planetary gear carrier 125 of a second planetary gear set which comprises a plurality of planetary gears 124 mounted on the carrier 125, a ring gear 123, and a sun gear 126.
  • the sun gear 126 of the second planetary gear set is coupled to the output shaft 145 by means of a pump /motor device 128 substantially as described above with reference to the embodiment of Figures 1-5.
  • a third planetary gear set comprises a plurality of planetary gears 122 mounted on a planetary gear carrier 120 which is fast with the intermediate shaft 138; a sun gear 121 secured to the output shaft 145; and the ring gear 123 which it shares with the second planetary gear set.
  • the reversing system C is operated to choose forward or reverse motion as desired.
  • the operation of the rotary transmission system D is the same for both forward and reverse rotation of the intermediate shaft 138, with the direction of rotation of the various rotary elements reversed as appropriate.
  • the shaft 138 rotates in the clockwise direction, rotating with it the ring gear 118 of the first planetary gear set and the planetary gear carrier 120 of the third planetary gear set .
  • the sun gear 116 of the first planetary gear set is fixed, rotation of the ring gear 118 will cause rotation of the planetary gear carrier 115 which in turn will rotate the drum 119 and the planetary gear carrier 125 of the second planetary set.
  • the sun gear 126 of the second planetary gear set will be stationary , and accordingly rotation of the planetary gear carrier 125 will cause rotation of the ring gear 123, thereby producing rotation of the sun gear 121 and output shaft 145.
  • rotation of the input shaft 102 will produce rotation of the output shaft 145 with an initial gear ratio of about 3 :1.
  • the gear ratio may be controlled by means of the pump/motor 128, and if desired a low gear ratio may be maintained by locking the sun gear 126 via the housing 127 of the device 128 using the brake mechanism 130.
  • FIG. 10 a third embodiment of the invention is shown.
  • the rotary transmission system D ' is identical to that described above with reference to Figure 6 (and like numerals will be used for like parts) except that the pump/motor 128 is driven from the input shaft 138 via a shaft 150, rather than from the output shaft 145.
  • the pump/motor 128 is used to vary the speed of rotation of the sun gear 126 relative to the speed of rotation of the pump/motor housing 127.
  • the reversing system C is provided at the outlet end of the gear box, and a conventional 3-speed mechanical gear box E is interposed between the torque convertor and the shaft 138 which constitutes the input to the rotary transmission system D ' .
  • the rotary transmission system is used to provide a smooth transition between the gear ratios provided by the mechanical gear box E, and thereby allows the speed of the output shaft to be progressively increased without significantly varying the rotational speed of the prime mover.
  • Such a system may be of . particular value in relatively heavy vehicles, for example trucks and passenger buses. «
  • the overall ratio of the rotary transmission system D ' is 1 :1.
  • the mechanical gears E provide ratios of 9 :1 , 6 :1 , and 3 :1 respectively .
  • the mechanical gear box E is operated to select a ratio of 9 :1 which is then applied to the shaft 138 to operate the rotary transmission system as described above with reference to Figure 6 to rotate the output shaft 145. Because the initial ratio of the rotary transmission - system D ' is 1 :1 , the overall transmission ratio of the complete CVT will initially be 9 :1. As the torque requirement of the vehicle reduces the brake 130 which is initially used to hold the sun gear 126 stationary is released, and the output of the pumping device 128 is throttled to progressively increase the speed of rotation of the sun gear 126 of the second planetary gear set.
  • the overall gear ratio of the CVT will still be 6 :1 despite the fact that the mechanical gear box E has been shifted from first to second gear.
  • the cycle is then repeated to reduce the overall ratio of the CVT to 3 :1 and again the mechanical gear box is shifted into third gear and the sun gear 126 is braked to standstill by the brake 130 before the power is re-applied.
  • the cycle is again repeated to produce an overall final CVT ratio of 1 :1 , being the combination of a reduction of 3 :1 produced by the third gear of the mechanical gear box E and a step up of 1 : 3 produced by the system D ' .
  • the reversing system C may incorporate a planetary gear set in the manner of the reversing system illustrated in Figure 6 to produce a final reduction in the output speed of the CVT, or may be in the form illustrated in Figure 10 in which the output shaft 145 is directly splined to the input crown wheel 107 of the reversing system, whereby the reversing system produces a 1 :1 transmission ratio.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Un système de transmission rotative comprend un premier train planétaire (18, 20-22) actionné par un arbre menant rotatif (14), un second train planétaire (24-26, 44) actionné par le premier train planétaire, et un troisième train planétaire (41-44) actionné par le second train planétaire. Un arbre mené (45) est actionné par le pignon central (43) du troisième train planétaire, et des moyens (28) sont destinés à mettre en rotation le pignon central (26) du second train planétaire, afin de modifier le rapport d'engrenage du système de transmission.
PCT/GB1991/000824 1990-05-25 1991-05-24 Transmission variable en continu Ceased WO1991019118A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9011806.8 1990-05-25
GB909011806A GB9011806D0 (en) 1990-05-25 1990-05-25 Rotary transmission system

Publications (1)

Publication Number Publication Date
WO1991019118A1 true WO1991019118A1 (fr) 1991-12-12

Family

ID=10676608

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1991/000824 Ceased WO1991019118A1 (fr) 1990-05-25 1991-05-24 Transmission variable en continu

Country Status (3)

Country Link
AU (1) AU7890391A (fr)
GB (1) GB9011806D0 (fr)
WO (1) WO1991019118A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993015337A1 (fr) * 1992-01-31 1993-08-05 Graham Edward Atkinson Systeme de transmission
US5830097A (en) * 1996-05-24 1998-11-03 General Dynamics Defense Systems, Inc. Multi-range with infinitely variable ratio in each range, hydromechanical transmission for off-road vehicles
DE10231669A1 (de) * 2002-07-12 2004-01-29 Wöhrl, Georg Stufenloses Getriebe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3405573A (en) * 1965-08-26 1968-10-15 Takekawa Toshio Variable speed mechanical hydraulic transmission mechanism especially suitable for heavy vehicles
US4196644A (en) * 1978-05-02 1980-04-08 Orshansky Transmission Corporation Hydromechanical transmission with compound planetary assembly
EP0143365A1 (fr) * 1983-11-22 1985-06-05 Friedrich Prof. Dr.-Ing. Jarchow Transmission continue de puissance
EP0222108A2 (fr) * 1985-09-18 1987-05-20 Michael Meyerle Transmission hydromécanique continue avec dérivation de puissance, notamment pour véhicules automobiles

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3405573A (en) * 1965-08-26 1968-10-15 Takekawa Toshio Variable speed mechanical hydraulic transmission mechanism especially suitable for heavy vehicles
US4196644A (en) * 1978-05-02 1980-04-08 Orshansky Transmission Corporation Hydromechanical transmission with compound planetary assembly
EP0143365A1 (fr) * 1983-11-22 1985-06-05 Friedrich Prof. Dr.-Ing. Jarchow Transmission continue de puissance
EP0222108A2 (fr) * 1985-09-18 1987-05-20 Michael Meyerle Transmission hydromécanique continue avec dérivation de puissance, notamment pour véhicules automobiles

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993015337A1 (fr) * 1992-01-31 1993-08-05 Graham Edward Atkinson Systeme de transmission
US5830097A (en) * 1996-05-24 1998-11-03 General Dynamics Defense Systems, Inc. Multi-range with infinitely variable ratio in each range, hydromechanical transmission for off-road vehicles
DE10231669A1 (de) * 2002-07-12 2004-01-29 Wöhrl, Georg Stufenloses Getriebe
DE10231669B4 (de) * 2002-07-12 2007-09-06 Wöhrl, Georg Stufenloses Getriebe

Also Published As

Publication number Publication date
AU7890391A (en) 1991-12-31
GB9011806D0 (en) 1990-07-18

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