WO2000057081A1 - Boite de vitesse automatique pour vehicule - Google Patents

Boite de vitesse automatique pour vehicule Download PDF

Info

Publication number
WO2000057081A1
WO2000057081A1 PCT/EP2000/002336 EP0002336W WO0057081A1 WO 2000057081 A1 WO2000057081 A1 WO 2000057081A1 EP 0002336 W EP0002336 W EP 0002336W WO 0057081 A1 WO0057081 A1 WO 0057081A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
gear set
web
motor vehicle
brake
Prior art date
Application number
PCT/EP2000/002336
Other languages
German (de)
English (en)
Inventor
Bernhard Drerup
Gerhard Gumpoltsberger
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2000057081A1 publication Critical patent/WO2000057081A1/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
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/037—Gearboxes for accommodating differential gearings

Definitions

  • the present invention relates to an automatically shiftable motor vehicle transmission with a first, a second and a third single-planet planetary gear set or with a third single-planet gear set and a planetary gear set composed of the first and the second single-planet planetary gear set as well as with three brakes and two clutches for shifting six forward gears and one reverse gear and with one input and one output shaft.
  • Such an automatic multi-speed transmission for vehicles is already known from EP 0 434 525 B1.
  • This transmission is characterized in particular by the fact that it has two power paths, namely a first power path that has a first fixed transmission ratio and contains the first and second clutch, and a second power path that has a second fixed transmission ratio that is higher than the first has in the same direction of rotation and contains the third clutch.
  • the object of the present invention is to provide an improved new type of transmission which avoids known disadvantages, meets the above-mentioned requirements and in particular enables a very good gradation between the first and second as well as the fifth and sixth gear. Furthermore, the transmission should be designed so that it allows any configuration and arrangement of the starting element as well as the drive and the output.
  • the generic motor vehicle transmission is designed such that the following components are constantly connected to one another:
  • the drive shaft is connected directly to the sun gear of the second planetary gear set or to the second sun gear of the composite planetary gear set.
  • the output shaft is connected to the ring gear of the third planetary gear set and the web of the first planetary gear set is connected to the ring gear of the second planetary gear set and to the sun gear of the third planetary gear set, or when the planetary gear set is assembled, the ring gear of the composite planetary gear set is connected to the sun gear of the third planetary gear set.
  • the ring gear of the first planetary gear set constantly with the web of the second planetary gear set or in the case of a composite planetary gear set, the first web is connected to the second web of the composite planetary gear set.
  • a transmission achieves an advantageous gradation between the first and second as well as between the fifth and sixth gear.
  • the transmission according to the invention advantageously enables three gear ratios ms slow and two gear ratios ms fast in fifth and sixth gear in the first to third gear.
  • Such a transmission is also suitable both for use in passenger cars and in commercial vehicles and is characterized by a low construction effort, i. That is, two clutches and three brakes, so that double shifts are avoided with sequential shifting and thus only one shift element is actuated in any shift within a group of gears.
  • the transmission according to the invention can advantageously be carried out in two versions, these differing from one another by different designs or connections of the individual planetary gear sets.
  • the first basic version essentially consists of three Emsteg planetary sets, which in turn can be arranged differently from one another.
  • the second basic version of the transmission according to the invention essentially consists of an Emsteg Planet set as well as a planet set (Ravigneaux set) composed of two single-web planet sets, which is also arranged at different points in the gearbox and is connected to the single-web planet set.
  • the drive shaft and the output shaft can be arranged coaxially to one another on opposite sides as well as both on the same side of the gear housing. Furthermore, the arrangement of the output from the transmission between the planetary gear sets and a clutch or between the Ravigneaux gear set and the single-planet gear set is also possible.
  • the first clutch be actuated in the fourth, fifth and sixth gear and the second clutch in the first, second, third and fourth gear.
  • the first brake is applied in the third and fifth gears and in the reverse gear, the second brake in the second and sixth gears and the third brake in the first gear and the reverse gear.
  • This advantageously means that only one shift element is changed in each shift between the first and fourth gear and between the fourth and sixth gear.
  • double switching is advantageously avoided with sequential switching.
  • FIG. 5 shows a transmission with coaxial input and output as shown in FIG. 1, but with a torque converter for a standard
  • Fig. 6 shows a transmission as shown in Fig. 3, but with an upstream torsional vibration damper and an integrated
  • FIG. 7 shows exemplary transmission series for one to 10 transmissions according to FIG. 1;
  • FIGS. 2 and 3 show exemplary transmission series for one to 14 transmissions according to FIGS. 2 and
  • 15 is a circuit diagram for a transmission according to the invention.
  • a transmission 1 according to the invention (FIG. 1) essentially consists of the Emsteg planetary gear sets 2, 3, 4 and the brakes 6, 7, 8 and the two clutches 9 and 10.
  • the drive shaft 11 is arranged coaxially with the output shaft 12.
  • the planetary gears 2, 3, 4 each consist of a sun gear, a web with planet gears and a ring gear, which are connected to one another as follows:
  • the drive shaft 11 is permanently connected to the sun gear 17 of the second planetary gear set 3.
  • the drive shaft 11 is also over the first clutch 9 can be connected to the web of the third planetary gear set 4 and via a further clutch 10 to the web 20 of the second planetary gear set 3 and via this web 20 to the ring gear 15 of the first planetary gear set 2.
  • the sun gear 13 of the first planetary gear set 2 can be locked on the housing of the transmission 1 via the brake 6.
  • the web 16 of the first planetary gear set 2 is connected to the ring gear 19 of the second planetary gear set 3 and the sun gear 21 of the third planetary gear set 4 and can be fixed on the housing via a brake 7.
  • the web 24 of the third planetary gear set can also be fixed via a brake 8.
  • the output shaft 12 is both as shown in Fig. 1 and all other representations of F g. 2 to 6 in permanent connection with the ring gear 23 of the third planetary gear set 4.
  • FIG. 2 In a second embodiment variant of the transmission according to the invention (FIG. 2) with likewise coaxial input and output 11, 12, instead of the first and second planetary gears, a composite planetary gear set 5 (Ravigneaux gear set) and a single-planet gear set 4 are provided. All elements which are common to FIGS. 1 to 6 or which perform the same functions are subsequently provided with the same reference symbols.
  • the drive shaft 11 is in constant drive connection with the second sun gear 28 of the composite planetary gear set 5.
  • the first sun gear 26 of the composite planetary gear set 5 can be locked on the housing by the brake 6.
  • the first and second webs 30 of the compound planetary gear set 5 are constantly connected to one another.
  • the ring gear 31 of the assembled planetary gear set can be locked in constant connection with the sun gear 21 of the single-web planetary gear set 4 and via the brake 7 on the housing.
  • the drive shaft 11 can be connected via the first clutch 9 and the second clutch 10 to the web 30 of the compound planetary gear set 5 and to the web 24 of the single-web planetary gear set 4.
  • the web 24 can also be locked by the third brake 8, the ring gear 23 of the planetary gear set 4 is also in constant connection with the output shaft 12.
  • the automatic transmission as shown in FIG. 3 essentially corresponds to a mirror-image version. tion of the transmission Fig. 2, wherein the single-planet planetary gear set 4 and the compound planetary gear set 5 are interchanged.
  • the output shaft 12 according to FIG. 3 is arranged between the single-web planetary gear set 4 and the first clutch 9.
  • FIG. 4 Another alternative arrangement of the output shaft 12 (Fig. 4) is that it is arranged between the second and third planetary gear sets 3 and 4.
  • the Emsteg planetary gear sets 2, 3 and 4 essentially correspond to a mirror-image representation according to FIG. 1.
  • the drive shaft 11 is in constant connection with the sun gear 17 of the second planetary gear set 3 and via the first clutch 9 with the web 24 of the third position. mesh set 4 and via a further coupling 10 to the web 20 of the second planetary gear set 3.
  • the output 12 takes place via the ring gear 23 of the third planetary gear set 4.
  • a torque converter 32 is provided between the drive shaft 11 and the first clutch 9.
  • the design of the planetary gear itself corresponds to the design according to FIG. 1.
  • the planetary gear set as shown in FIG. 3, is preceded by a torsional vibration damper 34 and started by the integrated starting brake 8.
  • the output shaft 12 is connected to the drive wheels 36 and 37 via the axle differential 35 .
  • the circuit diagram shows that the second clutch K2 is engaged in gears one to four and the first clutch K1 in gears four to six, both overlapping in fourth gear.
  • a brake B3, B2 or Bl is activated; brakes Bl and B2 in gears five and six respectively.
  • Reverse gear is switched by actuating brakes Bl and B3, a neutral position at standstill can be optionally set by switching brakes B2 and B3.

Landscapes

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

Abstract

L'invention concerne une boîte de vitesses automatique (1) pour véhicule, qui comprend soit un premier, un second et un troisième train planétaire à porte-satellite (2, 3, 4), soit un troisième train planétaire à porte-satellite (4) et un train planétaire (5) composé du premier et du second train planétaire à porte-satellite, ainsi que trois freins (6, 7, 8) et deux embrayages (9, 10) dont le couplage assure le passage de six rapports avant et d'un rapport arrière. Les trains planétaires suivants sont en permanence reliés les uns aux autres: l'arbre menant (11) est relié directement au pignon planétaire du second train planétaire ou au second pignon planétaire (28) du train planétaire (5), et l'arbre menant (12) à la couronne (23) du troisième train planétaire (4); le porte-satellite du premier train planétaire est relié à la couronne du second train planétaire et au pignon planétaire du troisième train planétaire ou bien, dans le cas d'un train planétaire composé (5), la couronne (31) de ce dernier (5) est reliée au pignon planétaire (21) du troisième train planétaire (4) et la couronne du premier train planétaire est reliée au porte-satellite du second train planétaire ou bien, dans le cas d'un train planétaire composé (5), le premier porte-satellite (30) est relié au second porte-satellite (30) de ce dernier (5).
PCT/EP2000/002336 1999-03-22 2000-03-16 Boite de vitesse automatique pour vehicule WO2000057081A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1999112481 DE19912481A1 (de) 1999-03-22 1999-03-22 Automatisch schaltbares Kraftfahrzeuggetriebe
DE19912481.7 1999-03-22

Publications (1)

Publication Number Publication Date
WO2000057081A1 true WO2000057081A1 (fr) 2000-09-28

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Family Applications (1)

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PCT/EP2000/002336 WO2000057081A1 (fr) 1999-03-22 2000-03-16 Boite de vitesse automatique pour vehicule

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DE (1) DE19912481A1 (fr)
WO (1) WO2000057081A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6589129B2 (en) 2001-10-01 2003-07-08 General Motors Corporation Powertrain having a multi-speed transmission with three planetary gear sets
US6648791B2 (en) 2001-09-26 2003-11-18 General Motors Corporation Family of multi-speed power transmission mechanisms having three planetary gear sets
US6652411B2 (en) 2001-09-26 2003-11-25 General Motors Corporation Multi-speed transmission family with three planetary gear sets and five rotating torque transmitting mechanisms

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19912480B4 (de) 1999-03-22 2006-03-16 Zf Friedrichshafen Ag Automatisch schaltbares Kraftfahrzeuggetriebe
DE19932613A1 (de) * 1999-07-13 2001-01-18 Zahnradfabrik Friedrichshafen Automatgetriebe
US6705967B2 (en) * 2001-02-21 2004-03-16 General Motors Corporation Six-speed transmission with three planetary gear sets and five torque transmitting mechanisms
DE10333430A1 (de) * 2003-07-23 2005-02-10 Zf Friedrichshafen Ag Mehrstufen-Automatgetriebe mit drei Planetenradsätzen
US7140997B2 (en) 2003-07-31 2006-11-28 Zf Friedrichshafen Ag Multi-stage automatic transmission with three planetary gearwheel assemblies
US6935984B2 (en) 2003-07-31 2005-08-30 Zf Friedrichshafen Ag Multi-stage automatic transmission with three planetary gearwheel assemblies
US6997845B2 (en) 2003-07-31 2006-02-14 Zf Friedrichshafen Ag Multi-stage automatic transmission with three planetary gearwheel assemblies
US7025703B2 (en) 2003-08-01 2006-04-11 Zf Friedrichshafen Ag Multistage automatic transmission with three planetary gear sets
US7179191B2 (en) 2003-08-01 2007-02-20 Zf Friedrichshafen Ag Multistage automatic transmission with three planetary gear sets
DE10340736A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340728A1 (de) 2003-09-04 2005-04-07 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340734A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340735A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340730A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340733A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340729A1 (de) 2003-09-04 2005-04-07 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340731A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10340732A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10350761A1 (de) 2003-10-30 2005-06-02 Zf Friedrichshafen Ag Mehrstufen-Automatgetriebe mit drei Planetenradsätzen
DE102004040905A1 (de) * 2004-08-24 2006-03-02 Zf Friedrichshafen Ag Mehrstufengetriebe
US7891171B2 (en) 2006-12-05 2011-02-22 GM Global Technology Operations LLC Hybrid catalyst for NOx reduction using fuel hydrocarbons as reductant
DE602007001184D1 (de) * 2007-01-23 2009-07-09 Sapa Placencia S L Mehrganggetriebe mit zwei Planetenradsätzen, zwei Kupplungen und zwei Bremsen
DE102019208556A1 (de) * 2019-06-12 2020-12-17 Robert Bosch Gmbh Getriebe für eine Hybridantriebsanordnung

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US5518465A (en) * 1994-11-14 1996-05-21 Hiraiwa; Kazuyoshi Planetary geartrain
JPH09112639A (ja) * 1995-10-16 1997-05-02 Jatco Corp 自動変速機用遊星歯車列及び自動変速機用歯車変速装置

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US4070927A (en) * 1976-06-04 1978-01-31 General Motors Corporation Planetary gearing arrangement for a transmission
DE2813223A1 (de) * 1978-03-25 1979-09-27 Daimler Benz Ag Gangwechselgetriebe
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JPH06323381A (ja) * 1993-02-27 1994-11-25 Volkswagen Ag <Vw> ３つの遊星歯車ユニットを備えた自動切換可能な多段変速機
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US5599251A (en) * 1995-09-27 1997-02-04 Ford Motor Company Six speed automatic transmission for automotive vehicles
US5707312A (en) * 1996-04-19 1998-01-13 General Motors Corporation Multi-speed power transmission

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Publication number Priority date Publication date Assignee Title
US2892361A (en) * 1956-03-01 1959-06-30 Borg Warner Transmission
JPH04290649A (ja) * 1991-03-20 1992-10-15 Nissan Motor Co Ltd 自動変速機の遊星歯車列
US5518465A (en) * 1994-11-14 1996-05-21 Hiraiwa; Kazuyoshi Planetary geartrain
JPH09112639A (ja) * 1995-10-16 1997-05-02 Jatco Corp 自動変速機用遊星歯車列及び自動変速機用歯車変速装置

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6648791B2 (en) 2001-09-26 2003-11-18 General Motors Corporation Family of multi-speed power transmission mechanisms having three planetary gear sets
US6652411B2 (en) 2001-09-26 2003-11-25 General Motors Corporation Multi-speed transmission family with three planetary gear sets and five rotating torque transmitting mechanisms
US6589129B2 (en) 2001-10-01 2003-07-08 General Motors Corporation Powertrain having a multi-speed transmission with three planetary gear sets

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