WO2015055174A2 - Transmission à double embrayage de type train planétaire - Google Patents

Transmission à double embrayage de type train planétaire Download PDF

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Publication number
WO2015055174A2
WO2015055174A2 PCT/DE2014/000532 DE2014000532W WO2015055174A2 WO 2015055174 A2 WO2015055174 A2 WO 2015055174A2 DE 2014000532 W DE2014000532 W DE 2014000532W WO 2015055174 A2 WO2015055174 A2 WO 2015055174A2
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
transmission
gear
dual
switching element
Prior art date
Application number
PCT/DE2014/000532
Other languages
German (de)
English (en)
Other versions
WO2015055174A3 (fr
Inventor
Mirko Leesch
Rico Resch
Jörg Müller
Original Assignee
Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr
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 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr filed Critical Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr
Publication of WO2015055174A2 publication Critical patent/WO2015055174A2/fr
Publication of WO2015055174A3 publication Critical patent/WO2015055174A3/fr

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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
    • 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
    • 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
    • F16H3/44—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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing 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
    • 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
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch

Definitions

  • the present invention relates to a dual-clutch transmission in
  • Planetary gearset is combined with a Ravigneaux planetary gear set.
  • a Ravigneaux planetary gear set For the realization of four forward gears, there for example the forward gears one to four, four power shift elements are needed.
  • double clutch transmissions in countershaft design for use in motor vehicles as a power shift transmission with two power shift elements and a plurality of jaw clutches and synchronizers as known for example from the patent DE 38 12 359 C3.
  • the load switching elements serve as Drive clutches to the output via one shaft each on the
  • Planetary gear design designed to take advantage of the high torque density of the planetary gear sets.
  • Multi-speed powershift transmission further comprises three planetary gear sets, wherein two planetary gear sets are reduced to a Ravigneaux planetary gear set.
  • the powershift transmission also includes nine positive clutches with
  • Synchronizers and two braking devices up to nine
  • forward gears and a reverse gear Provide forward gears and a reverse gear.
  • eight of the nine positive clutches are designed as two-way clutches with synchronizers, which each have two switching positions and a neutral position.
  • a forward gear is designed as a direct drive, in which both drive clutches are closed. For the realization of the forward gears low first forward gear to third forward gear five positive clutches are needed.
  • the object of the invention is to provide an improved dual-clutch planetary gearset, which is versatile
  • the invention provides a dual-clutch transmission according to the invention in Planetenradsatzbauweise ready, which is operational for a variety of applications.
  • Dual clutch transmission can be variably adjusted, so that the
  • Double clutch transmission in various drive concepts for motor vehicles can be used.
  • the improved dual-clutch transmission has a direct gear and three other gears whose gear ratios in
  • the dual-clutch transmission is therefore ideal for use in combination with internal combustion engines, in combination with
  • Electric machines can be integrated directly in the dual-clutch transmission, so that the dual-clutch transmission in combination with at least one electric machine is suitable for example for range extender applications.
  • the dual-clutch transmission according to the invention is made of the combination of a small number of load switching elements and planetary gear sets with high
  • Torque density formed whereby the space requirement compared to conventional dual clutch transmissions is reduced.
  • form-fitting switching elements which may include synchronization.
  • the dual-clutch transmission according to the invention in Planetenradsatzbauweise comprises in a common housing two power shift elements, a three-shaft gear as a planetary gear, a multi-shaft gear, in particular a four-shaft gear as a planetary gear composed of two planetary gear, four
  • the four-shaft transmission is reduced to a Ravigneaux planetary gear set.
  • the three-shaft transmission is associated with a first power shift element and the four-shaft transmission, a second load switching element, so that a first shaft of the
  • Three-shaft transmission by means of the first load switching element or a first shaft of the four-shaft transmission by means of the second load switching element with the drive of the dual-clutch transmission is connectable.
  • a second shaft of the three-shaft transmission with the housing of the dual-clutch transmission is connectable.
  • the second shaft of the three-shaft transmission continues to be connected to the first shaft of the three-shaft transmission.
  • a third switching element a second shaft of the four-shaft transmission is connectable to the housing.
  • a fourth switching element a third shaft of the four-shaft transmission is connectable to the housing.
  • a third shaft of the three-shaft transmission and a fourth shaft of the four-shaft transmission are connected to the output of the dual-clutch transmission or represent the output itself.
  • a first forward speed results from the operation of the first
  • the first shaft of the three-shaft transmission is connected to the drive and further the second shaft of the three-shaft transmission is connected to the housing and stopped.
  • the drive power is thus transmitted via the three-shaft gear, in particular via the first shaft and further via the third shaft to the output.
  • the drive torque is supported by the second shaft of the three-shaft transmission in the housing.
  • a second forward speed results from the actuation of the second
  • the first shaft of the four-shaft transmission is connected to the drive and furthermore the second shaft of the four-shaft transmission is connected to the housing and shut down.
  • the drive power is thus on the four-shaft gear, in particular on the first shaft and on transmitted to the output via the fourth shaft.
  • the drive torque is supported in the housing via the second shaft of the four-shaft transmission.
  • a third forward speed results from the operation of the first
  • the first shaft of the three-shaft transmission is connected to the drive and furthermore the second shaft of the three-shaft transmission is connected to the first shaft of the three-shaft transmission. Due to the fixed connection of the first and second shaft, the three-shaft transmission is blocked in itself. The drive power is thus transmitted via the blocked three-shaft gearbox to the output.
  • a fourth forward speed results from the actuation of the second
  • the first shaft of the four-shaft transmission is connected to the drive and furthermore the third shaft of the four-shaft transmission is connected to the housing and shut down.
  • the drive power is thus transmitted via the four-shaft gear, in particular via the first shaft and further via the fourth shaft to the output.
  • the drive torque is supported by the third shaft of the four-shaft gearbox in the housing.
  • the switching elements are preset such that the expected switching operation can be initiated by the operation of the load switching elements, without causing a traction interruption. That is, starting from a forward gear, the shift element required for the likely following forward gear is operated. Are the switching elements set according to the following forward gear, the load switching elements are actuated. There is always a change to the transmission of the drive power between the three-shaft transmission and four-shaft transmission and thus an alternating operation of the two load switching elements. The transmission of the drive power from the drive to the output thus takes place exclusively either via the first power shift element in conjunction with the three-shaft transmission or via the second power shift element in conjunction with the four-shaft transmission.
  • the first switching element is actuated before the switching operation and thus the second shaft of the three-shaft gearbox connected to the housing.
  • the third switching element is actuated before the switching operation and thus the second shaft of the four-shaft transmission connected to the housing.
  • the second switching element is actuated before the switching operation and thus the second shaft connected to the first shaft of the three-shaft transmission.
  • the fourth switching element is actuated before the switching operation and thus the third shaft of the four-shaft transmission connected to the housing.
  • Dual clutch transmission results in a particularly advantageous in terms of space requirements gear structure.
  • Three-shaft gear as a first sun gear with a first sun gear
  • the second shaft of the three-shaft gear as a first ring gear with a first ring gear
  • the third shaft of the three-shaft gear as a first ridge shaft with a first ridge as a planet carrier and at least three first planetary gears mounted thereon
  • the first planet gears are respectively engaged with the first sun gear and the first ring gear.
  • the first shaft of the four-shaft transmission as the second bridge shaft with a second bridge as a double planet carrier, on which at least one pair of planetary, preferably three Planetenradprese stored, the second shaft of the four-shaft transmission as a second sun gear with a second sun, the third wave of the four-shaft transmission third sun gear with a third sun gear and the fourth shaft of the four-shaft gear as a second ring gear with a second ring gear, wherein second inner planetary gears of the respective Planetenradcrues with the second sun gear and second outer planetary gears of the respective Planetenradbines and these second outer
  • Planet gears in turn are in engagement with the second ring gear and the third sun gear.
  • the three-shaft transmission thus comprises the first sun gear shaft with the first sun gear, the first land shaft with planet carrier and the at least three first planetary gears and the first ring gear with the first ring gear and the first switching element and the second switching element, wherein the first planet gears with the first sun gear and the first ring gear engaged.
  • the first Power shift element is the first sun gear and thus the first sun gear connected to the drive.
  • the drive is connected to the first sun-gear shaft and thus to the first sun-gear.
  • the first switching element By means of the first switching element, the first ring gear and thus the first ring gear with the housing of the dual clutch transmission is connectable.
  • the first switching element when the first switching element is closed, the first ring gear shaft is connected to the housing.
  • the first ring gear is connected to the first sun gear and thus the first ring gear with the first sun gear.
  • the second switching element when the second switching element is closed, the first
  • Ring gear shaft connected to the first sun gear shaft. Since the first switching element and the second switching element may not be closed simultaneously, the first ring gear is connectable to the housing of the dual clutch transmission or with the first sun gear.
  • the first bridge shaft is connected to the output of the
  • the four-shaft gear accordingly comprises the second sun gear shaft with the second sun gear, the third sun gear shaft with the third sun gear, the second land shaft with the second land, which is designed as a double planetary carrier and at least three Planetenradprese consisting of second inner planetary gears and second outer planetary gears, and the second ring gear with the second ring gear, and the third switching element and the fourth switching element.
  • the second inner planetary gears are engaged with the second sun gear and the second outer planetary gears, and these second outer planet gears further engage with the second ring gear and the third sun gear.
  • Power shift element is the second web shaft and thus the second web connectable to the drive.
  • the drive is connected to the second bridge shaft when the second load switching element is closed.
  • the third switching element By means of the third switching element, the second sun gear and thus the second sun can be connected to the housing.
  • the three-shaft gear can be designed such that the first shaft of the three-shaft gear as Clarradwelle with a first sun gear, the second shaft of the three-shaft gear as a ridge wave with a first ridge as a double planetary carrier on which at least three
  • Planetenradstande are stored, and the third wave of the three-shaft transmission is formed as a ring gear with a first ring gear. It turns out
  • said first inner planetary gears of Planetenradpare with the first sun gear and the first outer planet gears of Planetenradpare with the first ring gear are engaged. Accordingly, the first web can be connected to the housing by means of the first switching element. By means of the second switching element, therefore, the first web is connectable to the first sun gear.
  • the first ring gear is connected to the output of the
  • the four-shaft transmission can be designed such that at least three Planetenradstande are arranged on the second web, said second inner planetary gears with the second sun gear and each
  • the second ring gear can be divided into two separate ring gears, which are each connected to the output of the dual clutch transmission, so that in each case a separate second ring gear with the second outer planetary gears and another separate second ring gear is in engagement with the third planetary gears.
  • the four-shaft gear can be designed such that the second outer planetary gears are designed as stepped planets, so that each first stage planetary with the second inner planet gears and second stage planetary with the third sun gear engaged. Either the first stage planets or the second stage planets are still engaged with the second ring gear.
  • the first and the second switching element are combined to form a first double-acting switching unit, wherein either the first switching element or the second switching element can be closed.
  • a neutral position may be provided, wherein neither the first, nor the second switching element is closed.
  • the third and the fourth switching element are advantageously combined to form a second double-acting switching unit, wherein either the third switching element or the fourth switching element can be closed. Furthermore, a neutral position may be provided, wherein neither the third, nor the fourth
  • the first sun gear shaft and the second land shaft are arranged coaxially with one another.
  • the first sun gear shaft and the second land shaft may be arranged axially parallel to one another.
  • the three-shaft transmission and the four-shaft transmission can be arranged one behind the other or parallel to each other.
  • the first and the second load switching element can be arranged axially parallel to each other.
  • the output is coaxial with the first
  • Sun gear shaft and / or second web shaft arranged.
  • the electric machines of hybrid and electric vehicles are dimensioned smaller because no high torque reserves for starting and climbing ability must be maintained.
  • Dual clutch transmission becomes a gearbox for increasing the speed of a
  • the power shift elements are designed as friction clutches, with different types and friction lining pairings are possible.
  • the load switching elements can be preferably designed as a dry or wet-running disc or multi-plate clutches.
  • the switching elements are designed as jaw clutches, with additional synchronization devices can be provided. In the operation of the load switching elements methods are used, with which a change of the load switching elements for transmitting the drive power can be made as comfortable as possible. For starting operations, the load switching elements can be used. Alternatively, a further starting clutch may be provided, which is arranged between the drive unit and the dual-clutch transmission.
  • FIG. 1 shows a schematic representation of the transmission structure of the dual-clutch transmission according to the invention with a Weglogiktabelle for actuating
  • the dual-clutch transmission according to the invention in Planetenradsatzbauweise, shown in FIGURE 1, comprises two in a common housing
  • the drive 4 of the dual-clutch transmission can be connected to a first sun gear 6 of the three-shaft transmission 2 by means of a switchable first power shift element K1.
  • the three-shaft transmission 2 further comprises a first web shaft with a first web 7 on which first planetary gears 8 are arranged and are in engagement with a first ring gear 9 and the first sun gear 6.
  • the first web 7 is connected to the output 5 of the dual-clutch transmission.
  • the first ring gear 9 can be connected to the housing 1.
  • the first ring gear 9 with the first sun gear 6 is connected bar.
  • the drive 4 is connected by means of a switchable second load switching element K2 with a second web 10 of the four-shaft transmission 3.
  • the second web 10 is designed as a double planet carrier, on which Planetenradprese consisting of second inner planetary gears 11 and second outer planetary gears 12,
  • the second inner planetary gears 11 are arranged so that in each case the second inner planetary gears 11 are in engagement with the associated second outer planetary gears 12. Furthermore, the second inner planetary gears 11 are provided with a second sun gear 13 and the second outer planetary gears 12 with a third sun gear 14 and a second one
  • Ring gear 15 is engaged, so as to form a reduced planetary gear after the design of a Ravigneaux planetary gear set.
  • the second ring gear 15 is connected to the output 5 of the dual-clutch transmission.
  • the second sun gear 13 is connectable to the housing 1 of the dual-clutch transmission.
  • the third sun gear 14 is connectable to the housing 1 of the dual-clutch transmission.
  • FIG. 2 a schematic representation of the transmission structure of the dual-clutch transmission according to the invention with a shift logic table for actuating
  • the dual-clutch transmission according to the invention in Planetenradsatzbauweise shown in FIGURE 2, comprises in a common housing 1 two
  • the drive 4 of the dual-clutch transmission can be connected to a first sun gear 6 of the three-shaft transmission 2 by means of a switchable first power shift element K1.
  • the three-shaft transmission 2 further comprises a first web shaft with a first web 7, on which Planetenradpare consisting of first inner
  • Planetary gears 16 and first outer planetary gears 17, 17 are arranged so that Each of the first inner planet gears 16 are engaged with the associated first outer planetary gears 17. Continue to stand the first inner
  • the first ring gear 9 is connected to the output 5 of the dual-clutch transmission.
  • Switching element S1 the first web 7 is connected to the housing 1.
  • a second switching element S2 the first web 7 with the first sun gear. 6
  • the drive 4 is connected by means of a switchable second load switching element K2 with a second web 10 of the four-shaft transmission 3.
  • the second web 10 is designed as a double planet carrier, on which Planetenradprese consisting of second inner planetary gears 11 and second outer planetary gears 12 are arranged so that each of the second inner planetary gears 11 with the associated second outer planetary gears 12 are engaged.
  • the second inner planetary gears 11 are engaged with a second sun gear 13 and the second outer planetary gears 12 are engaged with a third sun gear 14 and a second ring gear 15 to form a reduced planetary gear according to the type of Ravigneaux planetary gearset.
  • the second ring gear 15 is connected to the output 5 of
  • Double clutch transmission connected.
  • the second sun gear 13 is connectable to the housing 1 of the dual-clutch transmission.
  • the third sun gear 14 With the
  • Housing 1 of the dual clutch transmission connectable.
  • FIG. 3 shows a schematic representation of the transmission structure of the dual-clutch transmission according to the invention with a shift logic table for actuating
  • the dual-clutch transmission according to the invention in Planetenradsatzbauweise, shown in FIGURE 1, comprises two in a common housing
  • the drive 4 of the dual-clutch transmission is by means of a switchable first
  • the three-shaft transmission 2 further comprises a first web shaft with a first web 7 on which first planetary gears 8 are arranged and are in engagement with a first ring gear 9 and the first sun gear 6.
  • the first web 7 is connected to the output 5 of the dual-clutch transmission.
  • the first ring gear 9 can be connected to the housing 1.
  • the first ring gear 9 with the first sun gear 6 is connectable.
  • the drive 4 is connected by means of a switchable second load switching element K2 with a second web 10 of the four-shaft transmission 3.
  • the second web 10 is designed as a double planet carrier, on which Planetenradprese consisting of second inner planetary gears 11 and second outer planetary gears 12 are arranged so that each of the second inner planetary gears 11 with the associated second outer planetary gears 12 are engaged. Furthermore, the second inner planet gears 11 with a second sun gear 13 and the second outer planetary gears 12 with a second ring gear 15 are engaged. Parallel to the second inner planetary gears 11 and second outer planetary gears 12, third planetary gears 18 are provided, which are mounted on the second web 10 and are in engagement with a third sun gear 14 and the second ring gear 15.
  • the second ring gear 15 may be divided to advantage.
  • the second ring gear 15 may be divided to advantage.
  • Ring gear 15 is connected to the output 5 of the dual-clutch transmission.
  • the second sun gear 13 is connectable to the housing 1 of the dual-clutch transmission.
  • the third sun gear 14 is connectable to the housing 1 of the dual-clutch transmission.

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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 transmission à double embrayage de type train planétaire comprenant dans un carter commun deux éléments de changement de vitesse sous charge, un engrenage à trois arbres réalisé sous la forme d'un engrenage planétaire, un engrenage à plusieurs arbres, en particulier un engrenage à quatre arbres réalisé sous la forme d'un engrenage planétaire composé de deux engrenages planétaires, quatre éléments de passage de vitesse ainsi qu'un entraînement et un arbre de sortie. Dans un mode de réalisation avantageux, l'engrenage à quatre arbres est réduit pour obtenir une transmission à roue planétaire Ravigneaux.
PCT/DE2014/000532 2013-10-18 2014-10-15 Transmission à double embrayage de type train planétaire WO2015055174A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013017326.4A DE102013017326B4 (de) 2013-10-18 2013-10-18 Doppelkupplungsgetriebe in Planetenradsatzbauweise
DEDE102013017326.4 2013-10-18

Publications (2)

Publication Number Publication Date
WO2015055174A2 true WO2015055174A2 (fr) 2015-04-23
WO2015055174A3 WO2015055174A3 (fr) 2015-06-11

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PCT/DE2014/000532 WO2015055174A2 (fr) 2013-10-18 2014-10-15 Transmission à double embrayage de type train planétaire

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DE (1) DE102013017326B4 (fr)
WO (1) WO2015055174A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110657203A (zh) * 2018-06-29 2020-01-07 比亚迪股份有限公司 变速器、动力驱动系统及车辆
CN110744998A (zh) * 2019-11-04 2020-02-04 广州市新域动力技术有限公司 叠式双转臂三速驱动系统
WO2022237775A1 (fr) * 2021-05-13 2022-11-17 江苏科技大学 Système de moteur de type silencieux à vitesse de rotation de sortie élevée

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017125068A1 (de) * 2017-10-26 2019-05-02 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Doppelkupplungsgetriebe

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