WO2004008001A1 - Transmission a variation continue a grand angle - Google Patents

Transmission a variation continue a grand angle Download PDF

Info

Publication number
WO2004008001A1
WO2004008001A1 PCT/KR2003/000745 KR0300745W WO2004008001A1 WO 2004008001 A1 WO2004008001 A1 WO 2004008001A1 KR 0300745 W KR0300745 W KR 0300745W WO 2004008001 A1 WO2004008001 A1 WO 2004008001A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
sun gear
clutch
ratio
pinion gears
Prior art date
Application number
PCT/KR2003/000745
Other languages
English (en)
Inventor
Jongwan Lee
Original Assignee
Jongwan Lee
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
Priority claimed from KR1020020040545A external-priority patent/KR20030082876A/ko
Application filed by Jongwan Lee filed Critical Jongwan Lee
Priority to AU2003219600A priority Critical patent/AU2003219600A1/en
Publication of WO2004008001A1 publication Critical patent/WO2004008001A1/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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0846—CVT using endless flexible members
    • 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
    • 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
    • F16H37/10—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 at both ends of intermediate shafts
    • F16H2037/105—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 at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing
    • F16H2037/107—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 at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing with switching means to provide three variator modes or ranges

Definitions

  • the present invention relates to continuously variable transmissions (CVT), and more particularly to the type of CVT that have wide coverage of speed ratio and high output torque.
  • CVT continuously variable transmissions
  • a CVT transmits power of a driving shaft to a driven shaft to get desirable torque and speed at the driven shaft in a infinitely variable ratio.
  • CVT There are many different types of CVT, but the most common type is belt-type.
  • a belt-type CVT is consisted of two pulleys and a belt, and transmits power by friction between pulleys and a belt. Transmittable torque is proportional to the coefficient of friction.
  • the ratio of radial-length/axial-length of pulley face should be small in order to change speed ratio by pushing pulley sheaves. Also the width of belt should be wide. Diameter of pulleys should be large for wide coverage of speed ratio.
  • Figure 1 is a schematic diagram illustrating a prior art that the inventor filed on Korean patent application No. 10-2002-04421.
  • Fig. 2 is a schematic diagram illustrating the first preferred embodiment of the present invention.
  • the first preferred embodiment is composed of variator (10) which transfers power from driving shaft (12) to driven shaft (14) in continuous speed ratio, a first planetary gear set (20) installed on said driven shaft (14), a second planetary gear set (30) installed on said driven shaft (14), a second clutch (52) installed on said driven shaft (14), a fourth clutch (54) installed on said driven shaft (14), a drive train of fixed ratio (40) installed between said driving shaft (12) and driven shaft (14), a seventh clutch installed on said driving shaft (12), and a first clutch (51) installed on said driving shaft (12).
  • a first sun gear (21) of said first planetary gear set (20) is fixed on said driven shaft (14).
  • First pinion gears (22) mesh with said first sun gear (21).
  • a first ring gear (23) meshes with said first pinion gears (22).
  • a first carrier (24) supports said first pinion gears (22) and rotates with said drive train (40).
  • a second sun gear (31) of said second planetary gear set (30) is installed on the same centerline with said first sun gear (21) to rotate in one body.
  • Second pinion gears (32) mesh with said second sun gear (31).
  • a second ring gear (33) meshes with said second pinion gears (32).
  • a second carrier (34) supports said second pinion gears (32) and is installed to rotate in one body with said first ring gear (23) and output shaft (18).
  • Said first and second sun gears (21, 31) may be one gear when module and tooth number are identical.
  • Said drive train (40) is composed of a first gear (41) installed rotatably on said driving shaft (12), a third gear (43) installed on said driven shaft (14) to rotate in one body with said first carrier (24), and a second gear (42) meshes with said first and third gears (41, 43).
  • Said first clutch (51) is installed to transfer selectively rotation of said driving shaft
  • Said second clutch (52) is installed to engage selectively said first ring gear (23) with said first carrier (24) in order to make said first planetary gear set (20) rotate in one body.
  • Said second clutch (52) can be located variously, because a planetary gear set rotates in one body by joining any two members together out of four members.
  • Said fourth clutch (54) is installed to lock selectively said second ring gear (33) on casing.
  • a seventh clutch (57) installed on said driving shaft (12) is starting clutch allowing speed ratio of —minimum value of this invention.
  • Tooth number ratio of said first gear (41) to said third gear (43) should be same with the minimum speed ratio of said variator (10). Tooth number ratio of said second ring gear (33) to said second sun gear (31) should be same with (speed of said first sun gear / speed of said first ring gear) -1 when speed ratio of said variator (10) is the maximum.
  • Speed of driven shaft (14) is reduced by second planetary gear set (30).
  • Now speed ratio of drive train (40) and speed ratio of variator (10) are same, and speeds of first gear (41) and driving shaft (12) are same. Tooth numbers of gears were selected carefully for this condition.
  • first clutch (51) is engaged in synchronized state, and fourth clutch (54) is disengaged.
  • ratio of variator (10) decreases down to minimum, speed of output shaft
  • an eighth clutch (58) may be added as shown Fig. 1, for reverse rotation of output shaft (18) by locking rotation of first carrier (24). Said eighth clutch can engage or disengage said drive train (40) with casing. Said eighth clutch (58) may be combined with said first clutch (51) as shown in Fig. 4 or Fig. 6. And said second clutch (52) and said fourth clutch (54) may be combined and may be shifted by one actuator as shown in Fig. 4. And said seventh clutch (57) may be installed on said output shaft (18) as shown in Fig. 4.
  • Fig. 6 is a schematic diagram illustrating the third preferred embodiment of the present invention. It comprises variator (10), a first planetary gear set (20), a second planetary gear set (30), a first clutch (51), a fourth clutch (54), and a drive train of fixed ratio (40). First sun gear (21) and second sun gear (31) are separated for independent rotation.
  • a sixth clutch (56) is installed between said two sun gears (21, 31) to unite them.
  • a fifth clutch (55) is installed to connect said first ring gear (23) to said second sun gear (31).
  • a third clutch (53) is installed to connect said first ring gear (23) to said second carrier (34).
  • the continuous ratio range of the third preferred embodiment is composed of four regions compared to three regions of said first preferred embodiment. Tooth numbers and speed ratio of said variator (10) are same as the first embodiment.
  • first clutch (51) For reverse drive of output shaft (18), first clutch (51) is engaged with casing, fourth and fifth clutches (54, 55) are engaged, and said third and sixth clutches (53, 56) are disengaged. Then seventh clutch (57) is engaged gradually. Range of speed ratio is (0.676—
  • said seventh clutch (57) may be replaced by a torque converter or others
  • said drive train (40) may be replaced by a chain drive or others.
  • Fig. 1 is a schematic diagram illustrating a prior art
  • Fig. 2 is a schematic diagram illustrating the first preferred embodiment of the present invention
  • Fig. 3 is a graph of the first embodiment illustrating the relationship among clutch states, variator ratio, and transmission ratio;
  • Fig. 4 is a schematic diagram illustrating the second preferred embodiment of the present invention
  • Fig. 5 is a graph of the second embodiment illustrating the relationship among clutch states, variator ratio, and transmission ratio;
  • Fig. 6 is a schematic diagram illustrating the third preferred embodiment of the present invention.
  • Fig. 7 is a graph of the third embodiment illustrating the relationship among clutch states, variator ratio, and transmission ratio
  • Present invention is suitable for a transmission of automobile. Also it is suitable to transforms speed and torque of engine to required speed and torque in continuous ratio for machining tools, industrial equipments, agricultural equipments, and etc.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une transmission à variation continue qui comprend une partie transmission à variation continue (10) conçue pour transmettre la puissance d'un arbre d'entraînement (12) à un arbre entraîné (14) à une vitesse continue; un premier dispositif à engrenage planétaire (20) qui équipe ledit arbre entraîné (14); un second dispositif à engrenage planétaire (30) qui équipe l'arbre entraîné (14); un deuxième embrayage (52) qui équipe l'arbre entraîné (14); un quatrième embrayage (54) qui équipe l'arbre entraîné (14); un élément réducteur de vitesse (40) installé entre l'arbre d'entraînement (12) et l'arbre entraîné (14); un septième embrayage installé dans l'arbre d'entraînement 12; et un premier embrayage (51) installé dans l'arbre d'entraînement (12). En outre, l'élément réducteur de vitesse (40) a un rapport de réduction tel que le rapport des vitesses entre un premier support (24) et une première roue solaire (21) peut être maximal, et que le rapport d'engrenage (vitesse d'une première roue solaire / vitesse d'une première couronne de train planétaire) entre une seconde couronne (31) de train planétaire et une seconde roue solaire (33) peut être 1 lorsque la vitesse de transmission de ladite partie transmission à variation continue (10) est maximale.
PCT/KR2003/000745 2002-07-12 2003-04-15 Transmission a variation continue a grand angle WO2004008001A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003219600A AU2003219600A1 (en) 2002-07-12 2003-04-15 Wide range continuously variable transmission

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2002-0040545 2002-07-12
KR1020020040545A KR20030082876A (ko) 2002-04-16 2002-07-12 광역 무단변속장치

Publications (1)

Publication Number Publication Date
WO2004008001A1 true WO2004008001A1 (fr) 2004-01-22

Family

ID=30113143

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2003/000745 WO2004008001A1 (fr) 2002-07-12 2003-04-15 Transmission a variation continue a grand angle

Country Status (2)

Country Link
AU (1) AU2003219600A1 (fr)
WO (1) WO2004008001A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2418235A (en) * 2004-09-20 2006-03-22 Torotrak Dev Ltd CVT with a compact variator which transmits less than 100% of engine power
ITMO20090043A1 (it) * 2009-02-20 2010-08-21 Bordini Engineering Srl Sistema a variazione continua di velocità
US8617020B2 (en) 2007-02-21 2013-12-31 Torotrak (Development) Limited Continuously variable transmission
CN104110475A (zh) * 2013-04-17 2014-10-22 福特全球技术公司 扭矩分配无级变速器
US9108511B2 (en) 2013-04-10 2015-08-18 Ford Global Technologies, Llc Transfer case

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01172679A (ja) * 1987-12-26 1989-07-07 Aisin Aw Co Ltd 無段変速機
JPH0392656A (ja) * 1989-09-04 1991-04-17 Bando Chem Ind Ltd 無段変速装置
US5967936A (en) * 1997-02-06 1999-10-19 Kia Motors Corporation Automatic variable transmission and hydraulic control system thereof
US6056661A (en) * 1999-06-14 2000-05-02 General Motors Corporation Multi-range transmission with input split planetary gear set and continuously variable transmission unit
US6135909A (en) * 1998-08-07 2000-10-24 Keiser; Fred Infinitely variable ratio transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01172679A (ja) * 1987-12-26 1989-07-07 Aisin Aw Co Ltd 無段変速機
JPH0392656A (ja) * 1989-09-04 1991-04-17 Bando Chem Ind Ltd 無段変速装置
US5967936A (en) * 1997-02-06 1999-10-19 Kia Motors Corporation Automatic variable transmission and hydraulic control system thereof
US6135909A (en) * 1998-08-07 2000-10-24 Keiser; Fred Infinitely variable ratio transmission
US6056661A (en) * 1999-06-14 2000-05-02 General Motors Corporation Multi-range transmission with input split planetary gear set and continuously variable transmission unit

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2418235A (en) * 2004-09-20 2006-03-22 Torotrak Dev Ltd CVT with a compact variator which transmits less than 100% of engine power
US8617020B2 (en) 2007-02-21 2013-12-31 Torotrak (Development) Limited Continuously variable transmission
ITMO20090043A1 (it) * 2009-02-20 2010-08-21 Bordini Engineering Srl Sistema a variazione continua di velocità
WO2010095111A1 (fr) * 2009-02-20 2010-08-26 Bordini Engineering S.R.L. Système de boîte de vitesse à variation continue
US9108511B2 (en) 2013-04-10 2015-08-18 Ford Global Technologies, Llc Transfer case
CN104110475A (zh) * 2013-04-17 2014-10-22 福特全球技术公司 扭矩分配无级变速器
US9546720B2 (en) 2013-04-17 2017-01-17 Ford Global Technologies, Llc Torque split continually variable transmission

Also Published As

Publication number Publication date
AU2003219600A1 (en) 2004-02-02

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