WO2017186427A1 - Boîte de vitesses à double embrayage à transmission intermédiaire - Google Patents

Boîte de vitesses à double embrayage à transmission intermédiaire Download PDF

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Publication number
WO2017186427A1
WO2017186427A1 PCT/EP2017/057152 EP2017057152W WO2017186427A1 WO 2017186427 A1 WO2017186427 A1 WO 2017186427A1 EP 2017057152 W EP2017057152 W EP 2017057152W WO 2017186427 A1 WO2017186427 A1 WO 2017186427A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
countershaft
transmission
switching element
idler gear
Prior art date
Application number
PCT/EP2017/057152
Other languages
German (de)
English (en)
Inventor
Jürgen WAFZIG
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
Priority to CN201780019213.0A priority Critical patent/CN108779834B/zh
Publication of WO2017186427A1 publication Critical patent/WO2017186427A1/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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0807—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with gear ratios in which the power is transferred by axially coupling idle 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0826—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output 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
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds

Definitions

  • the present invention relates to a dual-clutch transmission in countershaft design according to the preamble of patent claim 1.
  • a dual-clutch transmission consists of two trains or partial transmissions with different gear pairs, two power shift clutches, which are each associated with a partial transmission, a drive shaft and an output shaft and, depending on the number of gears from positive clutches.
  • the gears are arranged alternately in the two partial transmissions, so that it is possible to preselect a gear in the load-free partial transmission, while the torque is transmitted from the other partial transmission.
  • a gear shift is realized by transferring the torque to be transmitted from one power shift clutch to the other, so that the gears can be switched without load and without interruption of traction and without distortion of the shiftable gears.
  • the odd gears with one partial transmission and the even gears and the reverse gear are switchable with the other partial transmission.
  • the advantages of the dual-clutch transmission consist in an efficiency advantage over gearboxes in planetary design, a freer translation choice of the gears by the sub-transmission, the high speed suitability and in a sporty driving.
  • the known dual clutch transmission is provided that three double gear planes are provided and in each double gear plane in each case a loose wheel of the first and second countershaft is assigned to a fixed gear one of the transmission input shafts, wherein in each double gear plane at least one idler gear for at least two gears usable is, so that at least one Windungsgang is switchable via at least one switching element.
  • This dual-clutch transmission is particularly suitable for a front-transverse construction in a vehicle.
  • Another dual-clutch transmission which is suitable for a front-transverse construction in a vehicle, is known from DE 10 2007 049 267 A1 of the applicant; the input sides of the two clutches are connected to a drive shaft and whose output sides are each connected to one of two coaxial transmission input shafts.
  • the known transmission has at least one switching element for coupling the two transmission input shafts, wherein at least six powershift forward gears and at least one reverse gear are switchable and wherein three wheel planes or four wheel planes are arranged such that at least one lastschaltbarer Windungsgang switchable via the switching element for coupling the two transmission input shafts is.
  • the present invention has for its object to provide a dual clutch transmission in countershaft design, which is suitable for a front-transverse installation and allows a quick and comfortable direction change.
  • a transmission is proposed in countershaft design, comprising a first, connected to the output side of a first power shift clutch and designed as a solid shaft transmission input shaft, which is associated with a first partial transmission, a second, connected to the output side of a second power shift clutch and designed as a hollow shaft transmission input shaft, the one is associated with the second input gear and through which the first Getnebeeingangswelle is guided and a first and a second countershaft, each with a provided on the two countershaft driven gear, which is respectively coupled to a toothing of an output shaft, wherein on the first countershaft a first and a third switchable idler gear are arranged, which mesh to form a gear of a gear assigned to each wheel with a arranged on the first transmission input shaft first and third fixed gear, wherein on the first countershaft a second u nd a fourth switchable idler gear are arranged, which mesh to form a gear of a gear wheel associated with each one arranged on the second transmission input shaft second and
  • the fixed wheels, with which the loose wheels mesh to form an odd gear of the transmission associated wheel arranged on the first transmission input shaft, wherein the fixed wheels, which the idler gears of the transmission to form a straight gear of the transmission or the reverse gear associated wheel comb, are arranged on the second transmission input shaft.
  • the partial transmissions of the dual-clutch transmission can be reversed, so that the fixed wheels with which the idler gears mesh to form an odd gear of the transmission associated gear, are arranged on the second transmission input shaft and the fixed wheels with which the idler gears of the transmission to form a one straight gear of the transmission or the reverse gear associated with the wheel step, are arranged on the first transmission input shaft.
  • the transmission has seven form-fitting switching elements, which are preferably designed as synchronizers, by means of a first switching element, the second idler gear with the first countershaft releasably rotatably connected, by means of a second switching element, the fourth idler gear with the first countershaft is releasably rotatably connected, by means of a third switching element, the seventh idler gear with the second countershaft releasably rotatably connected, by means of a fourth Switching element, the sixth idler gear with the second countershaft releasably rotatably connected, by means of a fifth switching element, the third idler gear with the first countershaft releasably rotatably connected, by means of a sixth switching element, the first idler gear with the first countershaft releasably rotatably connected and wherein by means of a seventh switching element the fifth idler gear with the countershaft on which it is arranged, releasably rotatably connect
  • the transmission has an eighth form-locking switching element, by means of which the third idler gear with the fourth idler gear releasably rotatably connected.
  • an additional, seventh gear which is designed as a winding passage, can be realized.
  • the invention may be arranged to the drive according to the invention at least one electric machine for a hybrid drive on the drive side of the dual clutch with or without an additional coupling to the drive unit.
  • the electric machine can be operatively connected by means of a gear with a switchable idler gear of the transmission or switchable or fixedly coupled to a countershaft or be operatively connected to the second transmission input shaft.
  • FIG. 3 is a schematic representation of a second embodiment of a dual-clutch transmission according to the invention in countershaft design, which has seven forward gears and one reverse gear;
  • FIG. 9 shows a schematic illustration of a development of the transmission according to FIG. 5, in which an electric machine is integrated in the transmission, which is arranged on the drive side of the double clutch with an additional clutch to the drive unit; 10 shows a schematic representation of a further development of the transmission according to FIG. 5, in which an electric machine is integrated into the transmission, which is operatively connected by means of a toothed wheel to a switchable idler gear of the transmission;
  • a sixth shiftable idler gear L6 is arranged on the second countershaft VW2, which meshes with the arranged on the second transmission input shaft EW2 fourth fixed gear F4 to form a gear of the transmission gear
  • a seventh shiftable idler gear LR is arranged, which meshes with the one formed on the second transmission input shaft second fixed gear F2 intermeshing intermediate gear Z1 to form a gear stage assigned to a reverse gear of the gear iR.
  • the seventh shiftable idler gear LR can mesh with the second idler gear L2 arranged on the first countershaft to form a gear stage iR assigned to a reverse gear of the transmission.
  • the wheel stage i1 formed by the first idler gear L1 and the first fixed gear F1 corresponds to the wheel stage for generating the first forward gear of the transmission, wherein the wheel stage i2 of the wheel stage formed by the second idler gear L2 and the second fixed gear F2 for generating the second forward gear, the wheel stage i3 of the wheel stage formed by the third idler gear L3 and the third fixed gear F3 for generating the third forward gear, which is generated by the fourth idler gear L4 and the fourth fixed gear F4 formed wheel stage i4 the wheel stage to produce the fourth forward gear, the fifth gear L5 and the third fixed gear F3 or the additional additional fixed wheel formed wheel stage i5 the wheel stage to produce the fifth forward gear, by the sixth idler gear L6 and the fourth fixed gear F4 formed wheel stage i6 of the wheel stage to produce the sixth forward gear and wherein the formed by the seventh idler gear LR, the intermediate gear Z1 and the second fixed gear F2 and by the seventh idler gear LR and the second idler gear L2 wheel stage
  • the first and second, the third and fourth and the fifth and sixth switching elements are combined to form a double switching element DS1, DS2, DS3 with common actuator, which by the axial order second idler gear L2, fourth idler gear L4, third idler gear L3 , first idler gear L1 on the first countershaft VW1, the axial order seventh idler gear LR, sixth idler gear L6, fifth idler gear L5 on the second countershaft VW2, the axial Rethen discounted second fixed gear F2, fourth fixed gear F4 on the second transmission input shaft EW2 and the order third fixed gear F3, first fixed gear F1 on the first transmission input shaft EW1 is made possible.
  • the double switching elements can be designed as standard synchronous elements.
  • the transmission of FIG. 1 has six forward gears and one reverse gear. 2, in the case of the transmission 1 shown in FIG. 1, the first forward gear is obtained by closing the first power-shift clutch K1, ie when the first transmission input shaft is switched into the power flow. le EW1 and the sixth switching element S6, whereby the wheel stage i1 is switched to generate the first forward gear in the power flow.
  • the second forward speed is established by closing the second power-shift clutch K2, i. connected in the power flow second transmission input shaft EW2 and the first switching element S1, whereby the gear stage i2 is switched to generate the second forward gear in the power flow.
  • the third forward speed is switched by closing the first power-shift clutch K1 and the fifth shift element S5, whereby the gear stage i3 is switched to the power flow for generating the third forward speed.
  • the seventh shiftable idler gear LR can mesh with the second idler gear L2 arranged on the first countershaft to form the gear stage iR assigned to the reverse gear of the transmission, whereby the intermediate gear Z1 is omitted.
  • Double switching element DS3 combined with common actuator technology.
  • the gearshift corresponding to this transmission corresponds to the circuit diagram of FIG. 4.
  • FIGS. 8-12 illustrate ways of connecting an electric machine to the transmission according to FIG. 5.

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

Abstract

L'invention concerne une boîte de vitesses à double embrayage à transmission intermédiaire, comprenant un premier et un second arbre d'entrée de boîte de vitesses (EW1, EW2), et un premier et un second arbre d'intermédiaire (VW1, VW2). Un premier et un troisième pignon fou débrayables (L1, L3) sont disposés sur le premier arbre intermédiaire (VW1) et engrènent respectivement avec un premier et un troisième pignon fixe (F1, F3) disposés sur le premier arbre d'entrée de boîte de vitesses (EW1) pour former un étage de pignons (i1, i3) associé à un rapport de la boîte de vitesses ; un deuxième et un quatrième pignon fou (L2, L4) sont disposés sur le premier arbre intermédiaire (VW1) et engrènent respectivement avec un deuxième et un quatrième pignon fixe (F2, F4) disposés sur le second arbre d'entrée de boîte de vitesses pour former un étage de pignons (i2, i4) associé à un rapport de la boîte de vitesses ; un cinquième pignon fou débrayable (L5) est disposé sur le premier ou le second arbre intermédiaire et engrène avec un pignon fixe (F3, F5) disposé sur le premier arbre d'entrée de boîte de vitesses (EW1) pour former un étage de pignons (i5) associé à un rapport de la boîte de vitesses ; un sixième pignon fou débrayable (L6) est disposé sur le second arbre intermédiaire (VW2) et engrène avec le quatrième pignon fixe (F4) pour former un étage de pignons (i6) associé à un rapport de la boîte de vitesses ; un septième pignon fou débrayable (LR) est disposé sur le second arbre intermédiaire (VW2) et engrène avec un pignon intermédiaire (Z1) engrenant avec le deuxième pignon fixe (F2), ou engrène avec le second pignon fixe (F2), pour former un étage de pignons (iR) associé à une marche arrière de la boîte de vitesses.
PCT/EP2017/057152 2016-04-28 2017-03-27 Boîte de vitesses à double embrayage à transmission intermédiaire WO2017186427A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201780019213.0A CN108779834B (zh) 2016-04-28 2017-03-27 副轴形式的双离合变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016207221.8 2016-04-28
DE102016207221.8A DE102016207221A1 (de) 2016-04-28 2016-04-28 Doppelkupplungsgetriebe in Vorgelegebauweise

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WO2017186427A1 true WO2017186427A1 (fr) 2017-11-02

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PCT/EP2017/057152 WO2017186427A1 (fr) 2016-04-28 2017-03-27 Boîte de vitesses à double embrayage à transmission intermédiaire

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DE (1) DE102016207221A1 (fr)
WO (1) WO2017186427A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018220721B4 (de) 2018-01-31 2023-10-12 Ford Global Technologies, Llc Doppelkupplungsgetriebe für Kraftfahrzeuge mit Hybridantrieb
DE102019210829A1 (de) * 2019-07-22 2021-01-28 Zf Friedrichshafen Ag Getriebeanordnung, Hybrid-Getriebeanordnung, Hybrid-Antriebsstrang sowie Kraftfahrzeug
DE102020116543A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020209069A1 (de) 2020-07-20 2022-01-20 Magna Pt B.V. & Co. Kg Antriebsstrang
DE102020004394A1 (de) 2020-07-22 2022-01-27 Daimler Ag Hybridantriebseinrichtung für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug
CN112032263B (zh) * 2020-09-30 2024-04-05 重庆青山工业有限责任公司 一种双离合变速器结构
DE102020214521B4 (de) 2020-11-18 2024-05-08 Zf Friedrichshafen Ag Hybrid-Getriebe für einen Kraftfahrzeugantriebsstrang
DE102020131906A1 (de) 2020-12-02 2022-06-02 Audi Aktiengesellschaft Hybridantriebsstrang für ein hybridgetriebenes Fahrzeug
DE102020131917A1 (de) 2020-12-02 2022-06-02 Audi Aktiengesellschaft Hybridantriebsstrang für ein hybridgetriebenes Fahrzeug

Citations (6)

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Publication number Priority date Publication date Assignee Title
DE102007049265A1 (de) * 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102007049267A1 (de) 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102007049271A1 (de) 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
CN201502668U (zh) * 2009-07-21 2010-06-09 上海汽车集团股份有限公司 双离合器变速器
DE102009002354A1 (de) * 2009-04-14 2010-10-21 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102013211591A1 (de) * 2013-06-20 2014-12-24 Zf Friedrichshafen Ag Anordnung aus einem Getriebe und einer elektrischen Maschine für einen Hybridantrieb und Hybridantrieb

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007049269B4 (de) * 2007-10-15 2017-05-18 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
US8757020B2 (en) * 2011-08-03 2014-06-24 Gm Global Technology Operations, Llc Seven speed dual clutch transmission
CN103671748A (zh) * 2012-09-26 2014-03-26 重庆长安汽车股份有限公司 一种双离合器变速器传动装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007049265A1 (de) * 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102007049267A1 (de) 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102007049271A1 (de) 2007-10-15 2009-04-16 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE102009002354A1 (de) * 2009-04-14 2010-10-21 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
CN201502668U (zh) * 2009-07-21 2010-06-09 上海汽车集团股份有限公司 双离合器变速器
DE102013211591A1 (de) * 2013-06-20 2014-12-24 Zf Friedrichshafen Ag Anordnung aus einem Getriebe und einer elektrischen Maschine für einen Hybridantrieb und Hybridantrieb

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DE102016207221A1 (de) 2017-11-02
CN108779834B (zh) 2021-09-07
CN108779834A (zh) 2018-11-09

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