WO1993015337A1 - Power transmission - Google Patents
Power transmission Download PDFInfo
- Publication number
- WO1993015337A1 WO1993015337A1 PCT/AU1993/000043 AU9300043W WO9315337A1 WO 1993015337 A1 WO1993015337 A1 WO 1993015337A1 AU 9300043 W AU9300043 W AU 9300043W WO 9315337 A1 WO9315337 A1 WO 9315337A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear system
- continuously variable
- discrete step
- output
- drive
- Prior art date
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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
Definitions
- This invention relates to power transmission.
- this invention relates to the use of a continuously variable output gear system in a power transmission.
- hydraulic pump which in turn drives a motor for the wheels or tracks of a vehicle and further the hydraulic power
- the present invention provides
- a continuously variable output gear system arranged to transmit power to, or to receive power from, the discrete step ratio gear system and having an input shaft and an output shaft, and
- the present invention also provides a method of transmitting power comprising
- a continuous variable output gear system arranged to transmit power to, or receive power from, the discrete step ratio gear system and operating the continuously variable output gear system to produce an output shaft speed and/or torque varying by not greater than +/- 30%.
- the speed of rotation of the output shaft of the continuously variable output gear system can be varied to be about zero. This is a feature additional to varying by +/- 30% which is considered the desirable maximum variation under load conditions. However, under some load conditions when no output from the gearbox is required the output shaft speed may also be reduced to about zero.
- the means for varying should vary the output shaft speed and/or torque by not greater than +/- 20%.
- means may be provided for sensing the idle condition of an invention.
- the means for varying may be manually operated or may be operated in response to a parameter associated with output or load.
- the continuously variable output gear system comprises
- a sun gear a first shaft drive connected to the sun gear
- the discrete step ratio gear system may be a manual transmission, a power shift transmission or an automatic transmission.
- gearboxes as are commonly used in motor vehicles, front end loaders, ditch diggers, earth moving equipment, tractors, crawler tractors, harvesters and other agricultural equipment and in trucks and heavy haulage equipment have been found to be suitable.
- Said means for controlling preferably comprises a gear for controlling in drive engagement with a gear carried by the annulus and drive means for selectively controlling the speed and direction of rotation of said gear for controlling.
- Said drive means may be mechanically, electrically or hydraulically driven or may be driven via a torque converter.
- the annulus may be a crown wheel and the planetary gears may be pinions or the various gears may take any desired form.
- the gear system in accordance with this invention may also be applied to regenerative braking.
- Figure 1 is a schematic representation of a continuously variable gear system
- Figure 2 is a side view of a continuously variable gear system
- FIG. 3 is an exploded view of part of the gear system of Figure 2
- Figure 4 is a schematic representation of a vehicle including a transmission in accordance with this invention.
- FIG. 5 is a schematic representation of another vehicle including a transmission in accordance with this invention.
- FIG. 6 is a schematic representation of another vehicle including a transmission in accordance with this invention.
- FIG. 7 is a schematic representation of another vehicle including a transmission in accordance with this invention.
- the gear system shown schematically in Figure 1 is a continuously variable transmission 15 (CVT) and comprises a shaft 1 which may be an input or an output shaft, a sun gear 2 on the shaft 1 which is in drive engagement with planet gears 3, an annulus 4 which on the inside 5 is in drive engagement with the planet gears 3 and a control gear 6 which is in drive engagement with the outside 7 or the inside of the annulus.
- a shaft, not shown, which may be an output or an input shaft is connected to the planet gears 6.
- controlling the speed and direction of rotation of the annulus 4 by means of control gear 6 will vary the drive ratio.
- the drive means 25 may be mechanically, electrically or hydraulically driven or may be driven by a torque converter.
- the shaft 1 will be considered to be an input shaft 1 and the shaft 21 will be considered to be an output shaft 21.
- Input at the input shaft 1 will drive the sun gear 2 which will drive the planet gears 3 which will drive the annulus 4 via the inside 5 and the planet gears 3 will drive the output shaft 21.
- the drive ratio and direction of rotation at the output shaft 21 can be varied.
- the output shaft 21 can be varied from direct drive, to stop or in a reverse direction with respect to the input shaft 1. This can be achieved by driving or holding the control gear 6 to vary the rotational speed and direction of the annulus 4.
- a direct drive can be had by incorporating a lock up device between the input shaft 1 and the output shaft 21 and locating a clutch 26 or other freewheel or disengagement system between the drive means 25 and the control gear 6. In this instance, the control gear 6 will freely rotate and there will be direct drive from the input shaft 1 to the output shaft 21.
- the drive means 25 drives the control gear 6 at the same speed as, and in the same direction as, the input shaft 1, the planetary gears 3 will not rotate with respect to the annulus but will revolve with the annulus and there will be direct drive from the input shaft 1 to the output shaf't 21 and if desired a lock up can be effected.
- control gear 6 If the control gear 6 is driven at a selected lesser rotational speed then a selected ratio intermediate said normal ratio and direct drive can be obtained.
- a ratio of output to input can vary from the normal ratio to, in theory an infinite ratio and when the rotation of the control gear is in drive terms equal to the inverse of the normal ratio there will be no output shaft rotation, this being equivalent to a neutral drive.
- a clutch may be located on the input shaft and may be coupled to a locking device on the planetary gears such that when the clutch is engaged, it will engage the locking device to be locked up and when the clutch is released to a drive condition, the locking device will be released.
- gear systems use coupled together so that the output of one drives the input of another.
- velocity or torque may be increased.
- the drive means 25 is an hydraulic motor 31 and an hydraulic pump 32 is provided for driving the motor 31.
- FIG. 4 Also shown in Figure 4 is an engine 33, a clutch 34, a gearbox 36, a final drive 37 and wheels 38.
- the gearbox 36 is discrete step ratio gearbox which has multiple gears.
- the gearbox 36 is used in a conventional way but the motor 31 may be driven by the pump 32 to cause the continuously variable transmission 15 to vary the rotational speed or torque being delivered to the final drive.
- FIG. 5 is the same as Figure 4 except that a clutch 35 is shown which is differently positioned to clutch 34 and that the pump 32 rakes drive via gears 41 and 42.
- the gearbox 43 is a power shift transmission.
- FIG. 7 Also shown in Figure 7 are hydraulic lines 47 and 48, a pressure gauge 49 and a controller 51.
- the controller 51 is connected to the pump 32 to vary its output and the gauge 49 will show hydraulic pressure.
- a user may use the gauge 49 to give a measure of pressure and may adjust the controller 51 appropriately to drive the motor 31 to obtain the desired speed and/or torque. This may be done with respect to all or some of the gear ratios which the gearbox 36 or gearbox 43 can provide.
- the output shaft speed of the continuously variable transmission might be controlled to provide a braking effect on the engine during deceleration.
- the output shaft speed of the continuously variable transmission might be controlled so that the output shaft speed approaches zero as the engine approaches idle.
- the output shaft speed of the continuously variable transmission might be controlled so that the output shaft speed approaches zero under conditions in which high engine power is required to drive ancillary equipment such as an hydraulic pump for operation of non-tractive equipment such as a front end loader bucket or ditch digging equipment but little power is required for traction of the vehicle or where vehicle speed should be slowed or at least not substantially increase.
- ancillary equipment such as an hydraulic pump for operation of non-tractive equipment such as a front end loader bucket or ditch digging equipment but little power is required for traction of the vehicle or where vehicle speed should be slowed or at least not substantially increase.
- a foot pedal, or means or hand operated means may be provided to control the continuously variable output transmission.
- the present invention will find application in front end loaders, ditch diggers, earthmoving equipment, tractors, crawler tractors, harvesters and other agricultural equipment and in trucks and heavy haulage equipment.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Control Of Transmission Device (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP93903107A EP0623198A4 (en) | 1992-01-31 | 1993-02-01 | Power transmission. |
JP5512802A JPH07503055A (en) | 1992-01-31 | 1993-02-01 | power transmission device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AUPL0653 | 1992-01-31 | ||
AUPL065392 | 1992-01-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1993015337A1 true WO1993015337A1 (en) | 1993-08-05 |
Family
ID=3775961
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AU1993/000043 WO1993015337A1 (en) | 1992-01-31 | 1993-02-01 | Power transmission |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0623198A4 (en) |
JP (1) | JPH07503055A (en) |
WO (1) | WO1993015337A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2749130A1 (en) * | 1996-05-28 | 1997-12-05 | Claas Ohg | BALE PRESS FOR AGRICULTURAL CROP PRODUCT, WITH MULTIPLE DRIVE SYSTEMS |
EP1167818A2 (en) | 2000-06-21 | 2002-01-02 | ProRauta | A planetary gear transmission with variable ratio |
GB2431441A (en) * | 2005-10-22 | 2007-04-25 | Jcb Transmissions | Infinitely variable transmission with speed changing electric motor |
US20170167580A1 (en) * | 2015-12-10 | 2017-06-15 | Edi Bondioli | System comprising a mixer-wagon, for mixing and distributing fodder, and a mechanical power transmission unit for actuating the mixer-wagon |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3338950A1 (en) * | 1983-10-27 | 1985-05-23 | Zahnräderfabrik Renk AG, 8900 Augsburg | SHIP TRANSMISSION ARRANGEMENT |
WO1991019118A1 (en) * | 1990-05-25 | 1991-12-12 | Barton, Gordon, Page | Continuously variable transmission |
-
1993
- 1993-02-01 EP EP93903107A patent/EP0623198A4/en not_active Withdrawn
- 1993-02-01 WO PCT/AU1993/000043 patent/WO1993015337A1/en not_active Application Discontinuation
- 1993-02-01 JP JP5512802A patent/JPH07503055A/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3338950A1 (en) * | 1983-10-27 | 1985-05-23 | Zahnräderfabrik Renk AG, 8900 Augsburg | SHIP TRANSMISSION ARRANGEMENT |
WO1991019118A1 (en) * | 1990-05-25 | 1991-12-12 | Barton, Gordon, Page | Continuously variable transmission |
Non-Patent Citations (2)
Title |
---|
PATENT ABSTRACTS OF JAPAN, M-195, page 15; & JP,A,57 192 654 (TOSHINAGA ENDOU) 26 November 1982 (26.11.82), Abstract. * |
See also references of EP0623198A4 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2749130A1 (en) * | 1996-05-28 | 1997-12-05 | Claas Ohg | BALE PRESS FOR AGRICULTURAL CROP PRODUCT, WITH MULTIPLE DRIVE SYSTEMS |
EP1167818A2 (en) | 2000-06-21 | 2002-01-02 | ProRauta | A planetary gear transmission with variable ratio |
US6527671B2 (en) | 2000-06-21 | 2003-03-04 | Prorauta | Planetary gear transmission with variable ratio |
GB2431441A (en) * | 2005-10-22 | 2007-04-25 | Jcb Transmissions | Infinitely variable transmission with speed changing electric motor |
US20170167580A1 (en) * | 2015-12-10 | 2017-06-15 | Edi Bondioli | System comprising a mixer-wagon, for mixing and distributing fodder, and a mechanical power transmission unit for actuating the mixer-wagon |
US10495192B2 (en) * | 2015-12-10 | 2019-12-03 | Edi Bondioli | System comprising a mixer-wagon, for mixing and distributing fodder, and a mechanical power transmission unit for actuating the mixer-wagon |
Also Published As
Publication number | Publication date |
---|---|
EP0623198A4 (en) | 1995-06-07 |
JPH07503055A (en) | 1995-03-30 |
EP0623198A1 (en) | 1994-11-09 |
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