WO1992006316A1 - A gear device - Google Patents

A gear device Download PDF

Info

Publication number
WO1992006316A1
WO1992006316A1 PCT/NO1991/000126 NO9100126W WO9206316A1 WO 1992006316 A1 WO1992006316 A1 WO 1992006316A1 NO 9100126 W NO9100126 W NO 9100126W WO 9206316 A1 WO9206316 A1 WO 9206316A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheel
differential
annulus
drive
gear
Prior art date
Application number
PCT/NO1991/000126
Other languages
French (fr)
Inventor
Ken Lillevik
Original Assignee
Ken Lillevik
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 Ken Lillevik filed Critical Ken Lillevik
Publication of WO1992006316A1 publication Critical patent/WO1992006316A1/en

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
    • 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

  • the present invention relates to a gear device for steplessly variable transmission, comprising an epicyclic gear having a central sun wheel, planetary wheels, and an outer annulus and a planetary wheel carrier for mounting of the planetary wheels, and an output shaft, whereby the annulus is coupled to an appliance for controlled, adjustable rotation.
  • US Patent 4382392 describes a gear device which comprises two serially coupled epicyclic gears, for the achievement of a large variation of the transmission ratio.
  • the device is mechanically complicated and requires a large power consump ⁇ tion.
  • the present invention provides a gear device being charac ⁇ terized by the features appearing from the succeeding claim 1.
  • the invention is based on the acknowledgement that the annulus of the epicyclic gear should be mechanically driven, in order to keep the power consumption low.
  • a differential is interconnected for transmitting the input power to the sun wheel.of the epicyclic gear, from one of the driving wheels in the differential, whereby the other driving wheel is coupled to an adjustment wheel which can transmit a torque to the annulus, and whereby the adjustment driving appliance is used to determine the torque to be transmitted to the annulus.
  • the invention is not limited to a hydraulically operated adjustment, in that for instance also an electrical adjust ⁇ ment can be used.
  • the adjustment driving appliance will directly influence the rotation of the annulus of the epicyclic gear, but as the adjustment driving appliance is also coupled to the sun wheel of the epicyclic gear, indirectly via the differential, it will simultaneously influence the rotation of the sun wheel.
  • gear device When the gear device is used in a vehicle it is able to cause a steplessly variable shifting down, i.e. a reduced rotation ⁇ al speed of the output shaft from the epicyclic gear relatively to the input shaft of the differential. Also a shifting up, i.e. driving in overdrive, and reverse can be achieved.
  • Fig. 1 shows the gear device somewhat diagramatically, and the epicyclic gear and the differential are shown partly in an axial longitudinal section.
  • Fig. 2 shows diagrammatically the wheels incorporated in the epicyclic gear and a transmission wheel for controlling the annulus of the epicyclic gear, seen axially.
  • Fig. 1 shows an input shaft 1, which for instance may be directly coupled to a motor (internal combustion engine, electric motor) .
  • the shaft l. has a toothed gear 2, shown as a pinion, in engagement with a toothed ring on a differential housing 4.
  • the differential 3 contains in a known manner planetary wheels 5, usually two, being in driving engagement with two drive wheels 6 and 7, each having a drive shaft 8 and 9 protruding from the differential housing on respective sides thereof.
  • the epicyclic gear furthermore comprises planetary wheels 13, usually at least three in order to secure centering, distributed around the sun wheel 12.
  • the planetary wheels 13 are surrounded by an annulus 14. All the wheels are toothed. The mutual location and engagement of the wheels appear more clearly from Fig. 2, which shows the sun wheel 12, three planetary wheels 13 distributed with angular spacings of 120° and the annulus 14.
  • the annulus is also toothed on the outside, and is in engagement with a transmission wheel 20. The purpose of this will be further explained in the following.
  • the epicyclic gear comprises a planetary wheel carrier 11 which is in fixed connection with an output shaft 16, which for instance may be in driving connection with vehicle wheels, through a not shown differential.
  • the planetary wheels 13 are mounted for rotation in the planetary wheel carrier 11, and in order to achieve a bilateral and stable mounting of the planetary wheels 13 they are also mounted in a mounting disc 15.
  • the second drive shaft 9 protruding from the differential housing 4 carries an adjustment wheel 17, which via a transmission wheel 18 and a transmission shaft 19 is in connection with said transmission wheel 20 and thereby in connection with the annulus 14 of the epicyclic gear.
  • this comprises a control appliance, which in the example shown comprises a hydraulic pump 21, a hydraulic motor 22 being in driving connection with the adjustment wheel 17 through a shaft 23, and a control unit 24.
  • the motor can be coupled to the adjustment system anywhere between the drive shaft 9 and the annulus 14, and it will be appreciated that the hydraulic pump 21 and the motor 22 can be replaced by an electric motor.
  • the pump is driven by the input shaft 1.
  • the motor 22 can influence the adjustment wheel 17 in four different ways, by braking of the wheel, by keeping the wheel at rest ( no rotation ) , by driving the wheel at a higher rotational speed than that in which the wheel is driven by the differential 3, and by reversing the wheel.
  • the annulus 14 will of course be influenced cor ⁇ respondingly, and also the rotation of the sun wheel 12 will be influenced. Under the premise that the input shaft 1 rotates with a constant rotational speed braking of the adjustment wheel 17 ( and the annulus 14 ) will cause an increased rotational speed of the sun wheel 12 and of the planetary wheel carrier 11 ( and the output shaft 16 ) , i. e. the transmission ratio between the input shaft 1 and the output shaft 16 will be changed, and to a larger degree than if the adjustment merely influenced the adjustment wheel 17 and the annulus 14.
  • the pump When using a hydraulic pump for driving a hydraulic motor the pump may conveniently be an axial piston pump which may be adjusted steplessly.
  • the pump is controlled by the control unit 24, which must be adapted to what is desired to achieve with the gear device.
  • gear device according to the invention can be designed in many ways also with respect to the mechanical structure and that the shown transmission ratios within the epicyclic gear 10 and in the transmission from the shaft 9 to the annulus 14 via the adjustment wheel
  • the transmission wheels 18 and 20 and the shaft 19 can be chosen within wide limits.
  • the mutual location of the units can be different from that shown.
  • the motor 22, or an electric motor substituting it can be coupled anywhere in the adjustment system for the annulus 14, also directly thereto.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)
  • Retarders (AREA)

Abstract

A gear device for steplessly variable transmission, comprising an epicyclic gear (10) having a central sun wheel (12), planetary wheels (13), an outer annulus (14) and a planetary wheel carrier (11) for mounting of the planetary wheels, coupled to an output shaft (16). A differential (3) is intercoupled between an input shaft (1) and the sun wheel (12), whereby a drive gear (2) on the shaft is in drive connection with a differential housing (4), while a drive wheel (6) in the differential is in drive connection with the sun wheel (12), and a second drive wheel (7) in the differential is in drive connection with an adjustment wheel (17) which is coupled to the annulus (14). An adjustment appliance (21, 22, 23, 24) is provided for controlling the rotation of the annulus.

Description

A Gear Device .
The present invention relates to a gear device for steplessly variable transmission, comprising an epicyclic gear having a central sun wheel, planetary wheels, and an outer annulus and a planetary wheel carrier for mounting of the planetary wheels, and an output shaft, whereby the annulus is coupled to an appliance for controlled, adjustable rotation.
It is well known that the rotation of the annulus influences the transmission ratio between the sun wheel and the planetary wheel carrier. US Patent 4341132 describes a device as mentioned above. Operational energy for a hydraulic circuit is taken from the input shaft of the gear, which for instance may be the output shaft from a motor. Means are provided for adjusting the influence on the annulus, in order that it can be brought to rotate with different speeds or kept at rest. In order to achieve large transmission ratios the annulus has to rotate relatively fast, and all of the drive energy must be transmitted via the hydraulic system, which has a relatively small efficiency.
US Patent 4382392 describes a gear device which comprises two serially coupled epicyclic gears, for the achievement of a large variation of the transmission ratio. The device is mechanically complicated and requires a large power consump¬ tion.
The present invention provides a gear device being charac¬ terized by the features appearing from the succeeding claim 1.
The invention is based on the acknowledgement that the annulus of the epicyclic gear should be mechanically driven, in order to keep the power consumption low. This is achieved in that a differential is interconnected for transmitting the input power to the sun wheel.of the epicyclic gear, from one of the driving wheels in the differential, whereby the other driving wheel is coupled to an adjustment wheel which can transmit a torque to the annulus, and whereby the adjustment driving appliance is used to determine the torque to be transmitted to the annulus.
The invention is not limited to a hydraulically operated adjustment, in that for instance also an electrical adjust¬ ment can be used. The adjustment driving appliance will directly influence the rotation of the annulus of the epicyclic gear, but as the adjustment driving appliance is also coupled to the sun wheel of the epicyclic gear, indirectly via the differential, it will simultaneously influence the rotation of the sun wheel.
When the gear device is used in a vehicle it is able to cause a steplessly variable shifting down, i.e. a reduced rotation¬ al speed of the output shaft from the epicyclic gear relatively to the input shaft of the differential. Also a shifting up, i.e. driving in overdrive, and reverse can be achieved.
The invention will hereinafter be explained more detailed, with reference to the accompanying drawings, which show an example of an embodiment of a gear device according to the invention.
Fig. 1 shows the gear device somewhat diagramatically, and the epicyclic gear and the differential are shown partly in an axial longitudinal section.
Fig. 2 shows diagrammatically the wheels incorporated in the epicyclic gear and a transmission wheel for controlling the annulus of the epicyclic gear, seen axially.
Fig. 1 shows an input shaft 1, which for instance may be directly coupled to a motor (internal combustion engine, electric motor) . The shaft l.has a toothed gear 2, shown as a pinion, in engagement with a toothed ring on a differential housing 4. It will be appreciated that the shaft 1 can have any direction relatively to the differential housing 4. The differential 3 contains in a known manner planetary wheels 5, usually two, being in driving engagement with two drive wheels 6 and 7, each having a drive shaft 8 and 9 protruding from the differential housing on respective sides thereof.
One drive shaft 8 is in fixed connection with a central sun wheel 12 in an epicyclic gear 10. The epicyclic gear furthermore comprises planetary wheels 13, usually at least three in order to secure centering, distributed around the sun wheel 12. The planetary wheels 13 are surrounded by an annulus 14. All the wheels are toothed. The mutual location and engagement of the wheels appear more clearly from Fig. 2, which shows the sun wheel 12, three planetary wheels 13 distributed with angular spacings of 120° and the annulus 14. The annulus is also toothed on the outside, and is in engagement with a transmission wheel 20. The purpose of this will be further explained in the following. Moreover, the epicyclic gear comprises a planetary wheel carrier 11 which is in fixed connection with an output shaft 16, which for instance may be in driving connection with vehicle wheels, through a not shown differential. The planetary wheels 13 are mounted for rotation in the planetary wheel carrier 11, and in order to achieve a bilateral and stable mounting of the planetary wheels 13 they are also mounted in a mounting disc 15.
The second drive shaft 9 protruding from the differential housing 4 carries an adjustment wheel 17, which via a transmission wheel 18 and a transmission shaft 19 is in connection with said transmission wheel 20 and thereby in connection with the annulus 14 of the epicyclic gear.
All the crossed rectangles are diagrammetrical representa¬ tions of bearings, which for instance may be conventional ball or roller bearings. In order not to complicate the drawings a housing needed for mounting of the bearings and for keeping the gear device together as a unit is not shown.
It will appear from the above that when power is supplied to the gear device through the input shaft 1 it is possible to achieve rotation of both of the output drive shafts 8 and 9 from the differential 3. Except from a certain frictional loss a corresponding power can be taken out through the output shaft 16 from the epicyclic gear 10.
For controlling of the gear device this comprises a control appliance, which in the example shown comprises a hydraulic pump 21, a hydraulic motor 22 being in driving connection with the adjustment wheel 17 through a shaft 23, and a control unit 24. It will be appreciated that the motor can be coupled to the adjustment system anywhere between the drive shaft 9 and the annulus 14, and it will be appreciated that the hydraulic pump 21 and the motor 22 can be replaced by an electric motor. In the example shown the pump is driven by the input shaft 1. The motor 22 can influence the adjustment wheel 17 in four different ways, by braking of the wheel, by keeping the wheel at rest ( no rotation ) , by driving the wheel at a higher rotational speed than that in which the wheel is driven by the differential 3, and by reversing the wheel. The annulus 14 will of course be influenced cor¬ respondingly, and also the rotation of the sun wheel 12 will be influenced. Under the premise that the input shaft 1 rotates with a constant rotational speed braking of the adjustment wheel 17 ( and the annulus 14 ) will cause an increased rotational speed of the sun wheel 12 and of the planetary wheel carrier 11 ( and the output shaft 16 ) , i. e. the transmission ratio between the input shaft 1 and the output shaft 16 will be changed, and to a larger degree than if the adjustment merely influenced the adjustment wheel 17 and the annulus 14. Correspondingly, positive driving of the adjustment wheel 17 and the annulus 14 by means of the motor 22 will cause that the'rotational speed of the sun wheel 12 decreases, and the transmission ratio between the input shaft 1 and the output shaft 16 will also in this case be changed to a larger degree than by adjustment of the rotational speed of only the adjustment wheel 17 and the annulus 14.
When using a hydraulic pump for driving a hydraulic motor the pump may conveniently be an axial piston pump which may be adjusted steplessly. The pump is controlled by the control unit 24, which must be adapted to what is desired to achieve with the gear device.
When the gear device is to be used in a vehicle, no releas- able coupling ( clutch ) between the driving engine and the gear device is needed. For starting of the driving engine and running at idling speed without driving of the output shaft 16, provision may be made in order that the sun wheel 12 and the annulus 14 rotate in mutually opposite direction. nd at such rotational speeds that the planetary wheel carrier 11 and the output shaft do not rotate. Alternatively a releas- aole coupling may be employed, but this is not to be used during driving.
If an electric motor is employed in stead of the hydraulic mo-or 22, this may for braking of the adjustment wheel 17 be adapted to act as a generator.
For a certain rotational speed of the input shaft 1 there will for the shown embodiment of the gear device be a rotational speed for the drive wheel 7 in the differential, i.e. for the shaft 9 and the adjustment wheel 17, which implies that the planetary wheel carrier 11 and the output shaft 16 do not rotate. This rotational speed for the drive wheel 7 constitutes a partition between the two directions of rotation of the planetary wheel carrier 11 and the output shaft 16.
It will be appreciated that the gear device according to the invention can be designed in many ways also with respect to the mechanical structure and that the shown transmission ratios within the epicyclic gear 10 and in the transmission from the shaft 9 to the annulus 14 via the adjustment wheel
17 and the transmission wheels 18 and 20 and the shaft 19 can be chosen within wide limits. The mutual location of the units can be different from that shown. For instance the motor 22, or an electric motor substituting it, can be coupled anywhere in the adjustment system for the annulus 14, also directly thereto.

Claims

Claims .
1. A gear device for steplessly variable transmission, comprising an epicyclic gear (10) having a central sun wheel (12) , planetary wheels (13) , an outer annulus (14) and a planetary wheel carrier (11) for mounting of the planetary wheels, coupled to an output shaft (16), whereby the annulus
(14) is coupled to an adjustment wheel (17) which is coupled to an appliance (21,22,23,24) for adjusting the rotation of the annulus (14) by exercising of a torque, c h a r a c t e r i z e d i n that a differential (3) is intercoupled between an input drive shaft (1) and the sun wheel (12) , whereby a drive gear (2) on the drive shaft (1) is in drive connection with a differential housing (4) , while a first drive wheel (6) in the differential (3) is in drive connection with the sun wheel (12) , and that the adjustment wheel (17) also is in drive connection with a second drive wheel (7) in the differential.
2. A gear device as claimed in claim 1, c h a r a c t e r i z e d i n that the epicyclic gear (10) and the differential (3) are arranged coaxially relatively to each other.
3. A gear device as claimed in claim 1 or 2, c h a r a c t e r i z e d i n that the adjustment wheel (17) is situated outside of that end of the differential (3) facing away from the epicyclic gear (3) .
PCT/NO1991/000126 1990-10-01 1991-09-26 A gear device WO1992006316A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO904262A NO171328C (en) 1990-10-01 1990-10-01 GIR DEVICE
NO904262 1990-10-01

Publications (1)

Publication Number Publication Date
WO1992006316A1 true WO1992006316A1 (en) 1992-04-16

Family

ID=19893528

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO1991/000126 WO1992006316A1 (en) 1990-10-01 1991-09-26 A gear device

Country Status (3)

Country Link
AU (1) AU8660091A (en)
NO (1) NO171328C (en)
WO (1) WO1992006316A1 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4310158C1 (en) * 1993-03-29 1994-12-22 Braren Cyclo Getriebe Orbital gearbox with two output shafts
FR2807811A1 (en) * 2000-04-14 2001-10-19 Benoit Gresset Variator transmission for motor vehicle has casing containing shaft driving differential with rotation inverter and epicycloid gear train
WO2003016751A1 (en) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Universal holonomic transmission infinitely changing the torque
WO2009039590A1 (en) * 2007-09-28 2009-04-02 Stephen John Durnin A variable transmission
CN101680517B (en) * 2007-07-09 2012-03-21 艾顿株式会社 Reciprocating rotary power transforming apparatus
US20170356531A1 (en) * 2016-06-13 2017-12-14 Joe G. VILLARREAL Transmission assembly and method

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3119282A (en) * 1961-01-31 1964-01-28 Douglas D Raze Variable speed power transmission
CH658890A5 (en) * 1983-03-04 1986-12-15 Schweizerische Lokomotiv DRIVE DEVICE WITH VARIABLE TOTAL TRANSLATION.
US4913003A (en) * 1986-09-18 1990-04-03 Tervola Pentti J Stepless transmission
FR2638801A1 (en) * 1988-11-09 1990-05-11 Combastet Michel Power converter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3119282A (en) * 1961-01-31 1964-01-28 Douglas D Raze Variable speed power transmission
CH658890A5 (en) * 1983-03-04 1986-12-15 Schweizerische Lokomotiv DRIVE DEVICE WITH VARIABLE TOTAL TRANSLATION.
US4913003A (en) * 1986-09-18 1990-04-03 Tervola Pentti J Stepless transmission
FR2638801A1 (en) * 1988-11-09 1990-05-11 Combastet Michel Power converter

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4310158C1 (en) * 1993-03-29 1994-12-22 Braren Cyclo Getriebe Orbital gearbox with two output shafts
FR2807811A1 (en) * 2000-04-14 2001-10-19 Benoit Gresset Variator transmission for motor vehicle has casing containing shaft driving differential with rotation inverter and epicycloid gear train
WO2003016751A1 (en) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Universal holonomic transmission infinitely changing the torque
CN101680517B (en) * 2007-07-09 2012-03-21 艾顿株式会社 Reciprocating rotary power transforming apparatus
WO2009039590A1 (en) * 2007-09-28 2009-04-02 Stephen John Durnin A variable transmission
CN101868651A (en) * 2007-09-28 2010-10-20 斯蒂芬·约翰·杜宁 A variable transmission
US8668617B2 (en) 2007-09-28 2014-03-11 VRT Innovations Limited Variable transmission
US20170356531A1 (en) * 2016-06-13 2017-12-14 Joe G. VILLARREAL Transmission assembly and method
US10591028B2 (en) * 2016-06-13 2020-03-17 Joe G. VILLARREAL Transmission assembly and method

Also Published As

Publication number Publication date
NO904262L (en) 1992-04-02
AU8660091A (en) 1992-04-28
NO171328C (en) 1993-02-24
NO904262D0 (en) 1990-10-01
NO171328B (en) 1992-11-16

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