WO2014166541A1 - Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses - Google Patents

Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses Download PDF

Info

Publication number
WO2014166541A1
WO2014166541A1 PCT/EP2013/057611 EP2013057611W WO2014166541A1 WO 2014166541 A1 WO2014166541 A1 WO 2014166541A1 EP 2013057611 W EP2013057611 W EP 2013057611W WO 2014166541 A1 WO2014166541 A1 WO 2014166541A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
freedom
gear
idler gear
output
Prior art date
Application number
PCT/EP2013/057611
Other languages
German (de)
English (en)
Inventor
Johannes Ruschhaupt
Original Assignee
Fev Gmbh
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 Fev Gmbh filed Critical Fev Gmbh
Priority to DE112013006942.3T priority Critical patent/DE112013006942A5/de
Priority to PCT/EP2013/057611 priority patent/WO2014166541A1/fr
Priority to CN201380075507.7A priority patent/CN105102858B/zh
Publication of WO2014166541A1 publication Critical patent/WO2014166541A1/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
    • F16H2003/0803—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 countershafts coaxial with input or 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
    • 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
    • F16H2003/0933—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 with coaxial countershafts
    • 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
    • F16H2003/0938—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 with multiple gears on the input shaft directly meshing with respective gears 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
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds

Definitions

  • the invention relates to a transmission for motor vehicles, which is switchable between a plurality of gear shift stages, with two inputs and one output.
  • the two inputs can either be drive-connected with a drive motor, such as an internal combustion engine.
  • the dual-clutch transmission described therein comprises two input shafts which are each connectable to a drive motor with a friction clutch. Each of the input shafts is connectable via two pairs of gears optionally with an output shaft. Depending on which of the two friction clutches is closed, thus the drive torque is transmitted from the drive motor via the first input shaft to the output shaft or via the second input shaft to the output shaft. Thus, a total of four gear ratios of the transmission could be realized.
  • an intermediate shaft is provided, which is drivingly connected to one of the input shafts via a pair of gears with two fixed wheels. The intermediate shaft is also selectively connectable via one of two gear pairs with the other input shaft.
  • the powertrain can be formed from the first input shaft, the intermediate shaft, the second input shaft and the output shaft.
  • the powertrain may be formed of the second input shaft, the intermediate shaft, the first input shaft and the output shaft.
  • Dual-clutch transmissions have become an alternative to the conventional automatic transmissions with torque converter on the basis of their fuel consumption advantage Market established.
  • One reason for the fuel consumption advantage of the dual-clutch transmission is that for start-up no torque converter, but dry or wet-running clutches are used.
  • the torque converter as a starting element has two major advantages over clutches. It provides a high start-up performance through its boost in engine torque and is extremely thermally robust, which also endures long periods of creep or multiple starts on the mountain with a trailer.
  • especially the particularly efficient dual-clutch transmission with dry clutches are much more sensitive, which can lead to emergency shutdown of the transmission under unfavorable operating conditions.
  • DE 10 201 1050 083 A1 proposes a gearbox which has two inputs and one output, wherein between the two inputs a usable for forward gears, switchable connection is arranged and between the two inputs and the output in each case three usable for forward gears, switchable connections are arranged.
  • This transmission allows by its arrangement, in particular by the connection between the two inputs and the three connections between the two inputs and the output, a maximum number of gears with low mechanical complexity.
  • the two inputs and the output form three degrees of freedom of the gearbox, one degree of freedom of which covers all parts of a gearset, e.g. Shafts and gears, which are drivingly connected to each other without the operation of switching elements.
  • the three degrees of freedom can be coupled with each other via switchable connections.
  • a total of at least seven connections for forward gears are provided, so that only four shift forks are required for switching, even if there is still a connection for a reverse gear.
  • a shift fork switch two connections. Due to the connection between the two inputs, the three direct connections for forward gears between the first input and the output can be used in total for six forward gear shift stages of the transmission.
  • the three connections can be used to drive the output directly from the first input. Further, it is possible to drive the output through the second input by the second input via the connection between the two inputs drives the first input and the first input then via one of the three connections the output.
  • a total of twelve forward gears can be realized with four shift forks.
  • a so-called support circuit must be provided to realize the high number of gears.
  • the follower gear shift stage in During the drive via the other of the two inputs, the follower gear shift stage is engaged and then switched to the subsequent gear shift stage in which the drive takes place via the same input, which is also used to drive the outgoing.
  • engage the sequential gear shift stage means that those connections are required that are required for driving via the subsequent gear shift stage.
  • switching means that a clutch is closed to also direct the power path over the already inserted connections.
  • Object of the present invention is to provide a dual-clutch transmission of the type mentioned above, which realizes the highest possible number of gears in a small space, with no or only a small number of support circuits in the gearshift sequence are required.
  • the object is achieved by a transmission for motor vehicles which is switchable between a plurality of gear shift stages and has four degrees of freedom, wherein one of the degrees of freedom is a first input, one of the degrees of freedom is a second input, one of the degrees of freedom is an output and one of the degrees of freedom is an intermediate degree , Between the first input and the intermediate degree of freedom, at least two switchable connections that can be used for forward gears are provided. Between the insectssgrad and the output at least two usable for forward gears, switchable connections are provided. Between the second input and the output are at least two usable for forward gears, switchable connections provided and between the second input and the intermediate degree of freedom at least one usable for a forward gear, switchable connection is provided.
  • the transmission according to the invention has a total of four degrees of freedom, wherein one degree of freedom comprises all components of a gear set, z.
  • one degree of freedom comprises all components of a gear set, z.
  • an intermediate degree of freedom is provided, the components of which are not drive-connected to one of the inputs or to the output without actuation or closing of a switching element.
  • the two inputs with the intermediate degree of freedom are either drive-connected. At least two direct connections are provided between the second input and the output.
  • This arrangement of links and degrees of freedom allows three gear ratios to be provided in the low-speed to high-speed gearshift sequence following a direct gearshift stage between the second input and the output, always shifting from one input to the other in the gearshift sequence becomes.
  • the term "direct” gear shift stage refers to gear shift stages in which the power path is routed directly from one of the inputs, in this case the second input, via a connection to the output and no further degree of freedom is interposed. where the power path leads over at least three degrees of freedom.
  • a gear shift sequence with nine or more gear shift stages (gears) is possible in which no support circuit is required, ie in which can be blended in principle between two successive courses of an input to the other input.
  • a reverse gear can be realized that between the second input and the intermediate degree of freedom a switchable to realize the reverse gear connection is provided.
  • both inputs are each via a coupling, in particular a Friction clutch, with a prime mover, such as an internal combustion engine, connectable.
  • a coupling in particular a Friction clutch
  • a prime mover such as an internal combustion engine
  • the transmission is preferably controlled in such a way that, in the sequence of all successive forward gear shift stages used, the drive takes place alternately via one of the inputs. This avoids that so-called support circuits must be used.
  • the transmission is controlled in such a way that, in at least one group of at least three successive gear shift stages, the power path is always guided via one of the connections of the intermediate degree of freedom to the output.
  • At least two such groups of at least three successive gear shift stages are provided, between which a gear shift stage is provided, in which the power path is led from the second input via one of the connections between the second input and the output to the output.
  • FIG. 2 shows a diagram of the switching sequence of the transmission according to FIG. 1,
  • FIG. 3 shows a schematic representation of a first embodiment of a transmission according to the invention
  • FIG. 5 shows a schematic representation of a third embodiment of an inventive to the transmission according to the invention
  • FIG. 6 shows a schematic illustration of a fourth embodiment of a transmission according to the invention.
  • FIG. 7 shows a schematic representation of a fifth embodiment of a transmission according to the invention.
  • FIG. 8 shows a schematic representation of a sixth embodiment of a transmission according to the invention, and the torque curve in the case of a cross-fading switching operation.
  • FIG. 1 shows a schematic representation of the transmission according to the invention with four degrees of freedom, namely a first degree of freedom as first input 10, a second degree of freedom as second input 20, a third degree of freedom as intermediate degree of freedom 30 and a fourth degree of freedom as output 40.
  • Each degree of freedom comprises all parts, such as shafts and gears, which are drivingly connected together without the operation or the closing of switching elements and can rotate together or rotate.
  • the individual degrees of freedom 10, 20, 30, 40 can be drive-connected to one another via connections, the connections being switchable.
  • a compound may include switching elements and one or more gears here.
  • two connections 11, 12 are provided, which can be selectively switched to drive-connect the first input 10 to the intermediate degree of freedom 30.
  • connections 11, 12 are switchable such that the first input 10 and the intermediate degree of freedom 30 are not drive-connected to one another, ie no power can be conducted from the first input 10 to the intermediate degree of freedom 30.
  • two connections X1, X2 are also provided, which are selectively switchable in order to drive-connect the intermediate degree of freedom 30 to the output 40 or which can be switched such that the intermediate degree of freedom 30 is not connected to the output 40. is connected to the drive.
  • two switchable connections II, VI are also provided, which can be selectively switched to drive-connect the second input 20 to the output 40 or which can be switched such that the second input 20 and the output 40 are not drive-connected.
  • connection R Between the second input 20 and the intermediate degree of freedom 30 further two switchable connections 111, R are provided which are selectively switchable to drive connect the second input 20 to the intermediate degree of freedom 30 or switched such that the second input 20 does not interfere with the intermediate degree of freedom 30 is drive-connected.
  • the connection R also causes a reversal of direction to ensure a reverse gear. All other connections 11, 12, 111, X1, X2, II, VI serve to realize forward gears, provided that the connection R is not arranged in the power path.
  • the connections are switched such that each pair of connections between two degrees of freedom 10, 20, 30, 40 is switchable by means of a common shift fork. Thus, a total of four shift forks are required.
  • the first input 10 is also connectable via a first clutch C1 with a drive motor, not shown here.
  • the second input 20 is connectable via a second clutch C2 with the same drive motor.
  • FIG. 2 shows a schematic of the switching sequences for different gear shift stages (gears). For each gear shift stage is indicated, via which clutch C1, C2 is driven. For this purpose, the respective line indicates via which connection the power path runs.
  • the first clutch C1 is used for driving, the power path via the first connection 11 between the first input 10 and the intermediate degree of freedom 30, the first connection 111 between the intermediate degree of freedom 30 and the second input 20 and first connection II between the second input 20 and the output 40 extends.
  • the fourth gear (gear shift stage 4) is superimposed to the second clutch C2, wherein the power path from the second input 20 via the first connection 111 between the intermediate degree of freedom 30 and the second input 20 to the intermediate degree of freedom 30 and from there via the connection between the intermediate degree of freedom X1 30 and the output 40 leads to the output 40.
  • the seventh gear (gear shift stage 7) is blended to the first clutch C1, the power path from the second input 20 via the first connection 11 between the first input 10 and the intermediate degree of freedom 30 to the intermediate degree of freedom 30 and from there via the second connection between the intermediate degree of freedom X 30th and the output 40 to the output 40.
  • a reverse gear (gear shift stage R) can be achieved that via the first clutch C1, the power path from the first input 10 via the first connection 11 between the first input 10 and the intermediate degree of freedom 30 to the intermediate degree of freedom 30 and from there via the second connection R between the Intermediate degree of freedom 30 and the second input 20 to the second input 20 and further via the first connection II between the second input 20 and the output 40 to the output 40 extends.
  • the second connection R is connected between the intermediate degree of freedom 30 and the second input 20.
  • FIG. 3 shows a first embodiment of a wheel arrangement of a transmission according to the invention.
  • the first input 10 comprises a first input shaft 1 1, which is drive-connected via a first clutch C1 with a drive motor, not shown, usually an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein to simplify the present schematic illustration, the first clutch C1 is shown only with a first coupling element, which is part of the first input 10.
  • the intermediate degree of freedom 30 comprises an intermediate shaft 31, which is arranged rotatable parallel to the first input shaft 1 1.
  • a first Fixed wheel 32 and a second fixed wheel 33 is arranged on the intermediate shaft 31.
  • the two fixed wheels 32, 33 are fixedly connected to the intermediate shaft 31 and run with this.
  • the first fixed gear 32 meshes with a first idler gear 34 which is rotatably mounted on the first input shaft 1 1.
  • the second fixed gear 33 meshes with a second idler gear 35, which is likewise rotatably arranged on the first input shaft 1 1.
  • Via a first switching arrangement A which is part of the first input 10, the first idler gear 34 and the second idler gear 35 can optionally be connected in a rotationally fixed manner to the first input shaft 1 1.
  • neither of the two idler gears 34, 35 is non-rotatably connected to the first input shaft 1 1.
  • the first idler gear 34 and the second idler gear 35 can thus rotate relative to the first input shaft 1 1.
  • the first idler gear 34 and the first switching arrangement A are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the second idler gear 35 and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30.
  • the first idler gear 34 meshes with a third idler gear 36.
  • the second idler gear 35 meshes with a fourth idler gear 37.
  • the third idler gear 36 and the fourth idler gear 37 are arranged parallel to the first input shaft 1 1 and parallel to the intermediate shaft 31 rotatable.
  • the intermediate shaft 31, the fixed wheels 32, 33 and the loose wheels 34, 35, 36, 37 are part of the intermediate degree of freedom 30.
  • the output 40 comprises an output shaft 41 on which an output gear 42 is arranged, which is connectable to a drive arrangement for driving wheels of a motor vehicle, in particular with a differential gear.
  • the third idler gear 36 and the fourth idler gear 37 of the intermediate degree of freedom 30 are rotatably arranged on the output shaft 41.
  • the output shaft 41 can optionally be connected in a rotationally fixed manner to the third idler gear 36 or the fourth idler gear 37.
  • neither of the two idler gears 36, 37 is drive-connected to the output shaft 41, so that the third idler gear 36 and the fourth idler gear 37 are freely rotatable on the output shaft 41.
  • the third idler gear 36 and the third shifting arrangement C are thus part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the fourth idler gear 37 and the third shifting arrangement C form part of the second connection X2 between the intermediate degree of freedom 30 and the output 40th
  • the second input 20 includes a second input shaft 21, which is connectable via a second clutch C2 with the drive motor, not shown here. To simplify the illustration, only one switching element of the second clutch C2 is shown, wherein the second clutch C2 is designed as a friction clutch. The illustrated switching element of the second clutch C2 is also part of the second input 20.
  • a first fixed gear 22 and a second fixed gear 23 are fixed and rotate with the second input shaft 21st
  • the first fixed gear 22 meshes with a first idler gear 24, which is rotatably mounted on the output shaft 41.
  • the second fixed gear 23 meshes with a second idler gear 25, which is also rotatably mounted on the output shaft 41.
  • the output shaft 41 can optionally be rotatably connected to the first idler gear 24 or the second idler gear 25.
  • neither of the two idler gears 24, 25 is drive-connected to the output shaft 41, so that the first idler gear 24 and the second idler gear 25 are freely rotatable on the output shaft 41.
  • the first idler gear 24 and the fourth shifting arrangement D are part of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 and the fourth shifting arrangement D are part of the second connection VI between the second input 20 and the output 40.
  • the second fixed gear 23 further meshes with a third idler gear 26 which is rotatably mounted on the intermediate shaft 31.
  • the first fixed gear 22 meshes with the first idler gear 24 with a fourth idler gear 27, which is also rotatably mounted on the intermediate shaft 31.
  • the intermediate shaft 31 can be selectively connected to the third idler gear 26 or the fourth idler gear 27 rotatably.
  • neither the third idler gear 26 nor the fourth idler gear 27 is rotatably connected to the intermediate shaft 31, so that the third idler gear 26 and the fourth idler gear 27 can rotate freely on the intermediate shaft 31.
  • the third loose wheel 26 and the second shift arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 27 and the second shift gear B Arrangement B are part of the second connection R between the second input 20 and the intermediate degree of freedom 30.
  • the second input shaft 21, the fixed wheels 22, 23, and the idler gears 24, 25, 26, 27 are part of the second input 20th
  • Figure 4 shows a second embodiment of a gear set of a transmission according to the invention, wherein matching components are provided with the same reference numerals.
  • the elements of the first input 10 of the second embodiment are identical to the elements of the first input of the first embodiment.
  • the first input 10 comprises a first input shaft 1 1, which is drive-connected via a first clutch C1 with a drive motor, not shown, usually an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein to simplify the present schematic Dar- position, the first clutch C1 is shown only with a first coupling element, which is part of the first input 10.
  • the elements of the intermediate degree of freedom 30 differ in their arrangement to each other.
  • the first idler gear 34 and the second idler gear 35 are rotatably supported on the first input shaft 1 1 and mesh with the third idler gear 36 and the fourth idler gear 37, which are rotatably mounted on the output shaft 41.
  • the first idler gear 34 and the second idler gear 35 mesh with the two fixed wheels 32, 33 of the intermediate shaft 31, but the third idler gear 36 and the fourth idler gear 37.
  • the first idler gear 34 and the second idler gear 35 selectively connected to the first input shaft 1 1 rotatably.
  • neither of the two idler gears 34, 35 is non-rotatably connected to the first input shaft 1 1.
  • the first idler gear 34 and the second idler gear 35 can thus rotate relative to the first input shaft 1 1.
  • the first te idler gear 34 and the first switching arrangement A are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the second idler gear 35 and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30.
  • the intermediate shaft 31, the fixed wheels 32, 33 and the idler gears 34, 35, 36, 37 are part of the intermediate degree of freedom 30th
  • the output 40 comprises an output shaft 41 on which an output gear 42 is arranged, which is connectable to a drive arrangement for driving wheels of a motor vehicle, in particular with a differential gear.
  • the third idler gear 36 and the fourth idler gear 37 of the intermediate degree of freedom 30 are rotatably arranged on the output shaft 41.
  • the output shaft 41 can optionally be connected in a rotationally fixed manner to the third idler gear 36 or the fourth idler gear 37.
  • neither of the two idler gears 36, 37 is drive-connected to the output shaft 41, so that the third idler gear 36 and the fourth idler gear 37 are freely rotatable on the output shaft 41.
  • the third idler gear 36 and the third shifting arrangement C are thus part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the fourth idler gear 37 and the third shifting arrangement C form part of the second connection X2 between the intermediate degree of freedom 30 and the output 40.
  • the elements of the second input 20 are identical to the elements of the second input according to the first embodiment.
  • the fixed gears 22, 23 do not mesh with all the loose wheels 24, 25, 26, 27 of the second drive 20.
  • the first fixed gear 22 meshes with the first idler gear 24 on the output shaft 21 and the fourth idler gear 27 on the intermediate shaft 31st
  • the second fixed gear 23 meshes with the second idler gear 25 on the output shaft 41st
  • the output shaft 41 can optionally be rotatably connected to the first idler gear 24 or the second idler gear 25.
  • neither of the two idler gears 24, 25 is drive-connected to the output shaft 41, so that the first idler gear 24 and the second idler gear 25 are freely rotatable on the output shaft 41.
  • the first idler gear 24 and the fourth shifting arrangement D are part of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 and the fourth switching arrangement D are part of the second connection VI between the second input 20 and the output 40.
  • the second idler gear 25 further meshes with a third idler gear 26 which is rotatably mounted on the intermediate shaft 31
  • the first idler gear 24 meshes with the first fixed gear 22 with a fourth idler gear 27, which is also rotatably mounted on the intermediate shaft 31.
  • the intermediate shaft 31 can be selectively connected to the third idler gear 26 or the fourth idler gear 27 rotatably.
  • neither the third idler gear 26 nor the fourth idler gear 27 is rotatably connected to the intermediate shaft 31, so that the third idler gear 26 and the fourth idler gear 27 can rotate freely on the intermediate shaft 31.
  • the third idler gear 26 and the second switching arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 27 and the second switching arrangement B are part of the second connection R between the second input 20 and the intermediate degree of freedom 30.
  • the second input shaft 21, the fixed wheels 22, 23, and the idler gears 24, 25, 26, 27 are part of the second input 20th
  • the first embodiment and the second embodiment illustrate wheelset layouts for transversely mounted gear assemblies.
  • the following embodiments on the other hand, illustrate gear set layouts for longitudinally mounted gear assemblies. Corresponding components and elements are provided below with the same reference numerals used to the first embodiment and the second embodiment were.
  • the first input 10 of the third embodiment according to FIG. 5 comprises a first input shaft 1 1, which can be drive-connected via a first clutch C1 to a drive motor (not shown), as a rule an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein for simplification of the present schematic illustration, the first clutch C1 is shown only with a first coupling element, which Be is part of the first input 10.
  • the first fixed gear 12 meshes with a first idler gear 14, the second fixed gear 13 meshes with a second idler gear 15, wherein the two idler gears 14, 15 parallel to the first input shaft. 1 1 are rotatably arranged.
  • the first input shaft 1 1, the fixed wheels 12, 13 and the idler gears 14, 15 are elements of the first input 10th
  • the intermediate degree of freedom 30 comprises an intermediate shaft 31 about which the two loose wheels 14, 15 of the first input 10 are rotatably arranged.
  • the intermediate shaft 31 carries a first fixed wheel 32.
  • a first idler gear 34 is rotatably arranged.
  • the first idler gear 32 meshes with a second idler gear 35.
  • the first idler gear 34 meshes with a third idler gear 36.
  • the second idler gear 35 and the third idler gear 36 are rotatably connected to each other and are arranged together in rotation parallel to the intermediate shaft 31.
  • the intermediate shaft 31, the first fixed gear 32 and the loose wheels 34, 35, 36 are part of the intermediate degree of freedom 30th
  • the second input 20 includes a second input shaft 21, which is arranged coaxially with the first input shaft 1 1 and which is connectable via a second clutch C2 with the drive motor, not shown here.
  • a second clutch C2 with the drive motor, not shown here.
  • the illustrated switching element of the second clutch C2 is also part of the second input 20.
  • On the second input shaft 21 are four fixed wheels, lend a first fixed wheel 22, a second fixed gear 23, a third fixed gear 28 and a fourth fixed gear 29.
  • the first fixed 22 meshes with a first idler gear 24, which is arranged coaxially with the intermediate shaft 31 of the intermediate degree of freedom 30 rotatably.
  • the second fixed gear 23 meshes with a second idler gear 25 which is also rotatably arranged coaxially with the intermediate shaft 31 of the intermediate degree of freedom 30.
  • the third fixed gear 28 meshes with a third idler gear 26, which is also arranged coaxially rotatable with the intermediate shaft 31 of the intermediate degree of freedom.
  • the fourth fixed gear 29 meshes via a not shown here wheel with a fourth idler gear 27, which is also arranged coaxially to the intermediate shaft 31 of the intermediate degree of freedom 30 rotatably.
  • the second input shaft 21, the fixed wheels 22, 23, 28, 29th as well as the loose wheels 24, 25, 26, 27 are elements of the second input 20th
  • an output shaft 41 is rotatably mounted, which is rotatably connected to an output gear 42, which is connectable to a drive assembly for driving wheels of a motor vehicle, in particular with a differential gear.
  • either the first idler gear 14 or the second idler gear 15 of the first input 10 can be non-rotatably connected to the intermediate shaft 31 or switched such that neither of the idler gears 14, 15 is connected to the intermediate shaft 31.
  • the switching arrangement A and the first idler gear 14 are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the second idler gear 15 and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30th
  • the third idler gear 26 or the fourth idler gear 27 of the second input 20 can be connected to the intermediate shaft 31 of the intermediate degree of freedom 30.
  • the second switching arrangement B is switchable such that neither the third idler gear 26 nor the fourth idler gear 27 is drive-connected to the intermediate shaft 31.
  • the third idler gear 26 and the second switching arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 27 and the second switching arrangement B are part of the second connection R between the second input 20 and the intermediate degree of freedom 30.
  • a third shift arrangement C optionally the first fixed wheel 32, and thus the intermediate shaft 31, the intermediate degree of freedom 30 or the first idler gear 34 of the intermediate degree of freedom 30, can be connected in a rotationally fixed manner to the output shaft 41.
  • the first fixed gear 32 and the third shifting arrangement C are part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the first idler gear 34 and the third shifting arrangement C are part of the second connection X2 between the Intermediate degree of freedom 30 and the output 40.
  • first idler gear 24 or the second idler gear 25 of the second input 20 can be connected to the output shaft 41.
  • first idler gear 24 and the fourth shifting arrangement D are elements of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 and the fourth switching arrangement D are elements of the second connection VI between the second input 20 and the output 40.
  • the first input 10 of the fourth embodiment according to FIG. 6 comprises a first input shaft 1 1, which can be drive-connected via a first clutch C1 to a drive motor (not shown), as a rule an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein to simplify the present schematic illustration, the first clutch C1 is shown only with a first coupling element, which is part of the first input 10.
  • the first fixed gear 12 meshes with a first idler gear 14, the second fixed gear 13 meshes with a second idler gear 15, wherein the two idler gears 14, 15 parallel to the first input shaft 1 1 are rotatably arranged.
  • the first input shaft 1 1, the fixed wheels 12, 13 and the idler gears 14, 15 are elements of the first input 10.
  • the intermediate degree of freedom 30 comprises an intermediate shaft 31 about which the two loose wheels 14, 15 of the first input 10 are rotatably arranged.
  • the intermediate shaft 31 carries a first fixed gear 32.
  • a first idler gear 34 is rotatably arranged.
  • the first idler gear 32 meshes with a second idler gear 35.
  • the first idler gear 34 meshes with a third idler gear 36.
  • the second idler gear 35 and the third idler gear 36 are connected to each other in a rotationally fixed manner and are rotatably arranged together parallel to the intermediate shaft 31.
  • a second fixed wheel 33 is further provided that meshes via a not-shown wheel with a fourth idler gear 37 that is coaxial with the idler gears 35, 36 rotatably arranged.
  • the intermediate shaft 31, the fixed wheels 32, 33 and the idler gears 34, 35, 36, 37 are part of the intermediate degree of freedom 30.
  • the second input 20 includes a second input shaft 21, which is arranged coaxially with the first input shaft 1 1 and which is connectable via a second clutch C2 with the drive motor, not shown here.
  • a second clutch C2 with the drive motor, not shown here.
  • the illustrated switching element of the second clutch C2 is also part of the second input 20.
  • On the second input shaft 21 are seated two fixed gears, namely a first fixed wheel 22 and a second fixed gear 23.
  • the first fixed gear 22 meshes with a first idler gear 24 which coaxially to the intermediate shaft 31 of the intermediate degree of freedom 30 is rotatably arranged.
  • the second fixed gear 23 meshes with a second idler gear 25 which is also rotatably arranged coaxially with the intermediate shaft 31 of the intermediate degree of freedom 30.
  • the second input shaft 21, the fixed wheels 22, 23 and the loose wheels 24, 25 are elements of the second input 20.
  • an output shaft 41 is rotatably mounted, which is non-rotatably connected to an output gear 42, which is connectable to a drive arrangement for driving wheels of a motor vehicle, in particular with a differential gear.
  • either the first idler gear 14 or the second idler gear 15 of the first input 10 can be non-rotatably connected to the intermediate shaft 31 or switched such that neither of the idler gears 14, 15 is connected to the intermediate shaft 31.
  • the switching arrangement A and the first idler gear 14 are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the second idler gear 15 and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30th
  • the second idler gear 35 of the intermediate degree of freedom 30 or the fourth idler gear 37 of the intermediate degree of freedom 30 can optionally be connected to the second input shaft 21.
  • the second switching arrangement B is switchable such that neither the second idler gear 35 nor the fourth idler gear 37 of the Intermediate degree of freedom 30 is drivingly connected to the second input shaft 21.
  • the second idler gear 35 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 37 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the second connection R between the second input 20 and the intermediate degree of freedom 30.
  • a third shift arrangement C optionally the first fixed wheel 32, and thus the intermediate shaft 31, the intermediate degree of freedom 30 or the first idler gear 34 of the intermediate degree of freedom 30, can be connected in a rotationally fixed manner to the output shaft 41.
  • the first idler gear 34 and the third shifting arrangement C are part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the first fixed gear 32 and the third shifting arrangement C form part of the second connection X2 between the intermediate degree of freedom 30 and the output 40.
  • either the first idler gear 24 or the second idler gear 25 of the second input 20 can be connected to the output shaft 41.
  • the first idler gear 24 of the second input 20 and the fourth shifting arrangement D are elements of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 of the second input 20 and the fourth switching arrangement D are elements of the second connection VI between the second input 20 and the output 40th
  • the first input 10 of the fifth embodiment according to FIG. 7 comprises a first input shaft 1 1, which can be drive-connected via a first clutch C1 to a drive motor (not shown), as a rule an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein to simplify the present schematic illustration, the first clutch C1 is shown only with a first coupling element, which is part of the first input 10.
  • the intermediate degree of freedom 30 comprises a first intermediate shaft 31, which carries three fixed wheels, namely a first fixed gear 32, a fourth fixed gear 38 and a fifth fixed gear 39.
  • a second intermediate shaft 31 ' is rotatably mounted, which carries two fixed wheels, namely a second fixed wheel 33 and a third fixed wheel 34 '.
  • the fourth fixed gear 38 meshes with a fifth idler gear 38 'which is rotatably disposed about the first input shaft 1 1.
  • the fifth fixed gear 39 meshes with a sixth idler gear 39 ', which is also rotatably disposed about the first input shaft 1 1.
  • the first fixed gear 32 meshes with a second idler gear 35 and the third fixed gear 34 'with a third idler gear 36.
  • the second idler gear 35 and the third idler gear 36 are rotatably connected to each other and are rotatable together in parallel to the intermediate shafts 31, 31' arranged.
  • the second fixed gear 33 on the second intermediate shaft 31 ' is drivingly connected via a not-shown wheel with a fourth idler gear 37, which is arranged coaxially to the idler gears 35, 36 rotatably.
  • the intermediate shafts 31, 31 ', the fixed wheels 32, 33, 34', 38, 39 and the loose wheels 35, 36, 37, 38 ', 39' are part of the intermediate degree of freedom 30th
  • the second input 20 includes a second input shaft 21, which is arranged coaxially with the first input shaft 1 1 and which is connectable via a second clutch C2 with the drive motor, not shown here.
  • a second clutch C2 with the drive motor, not shown here.
  • the illustrated switching element of the second clutch C2 is also part of the second input 20.
  • On the second input shaft 21 sitting two fixed wheels, namely a first fixed gear 22 and a second fixed gear 23.
  • the first fixed gear 22 meshes with a first idler gear 24, which coaxial with the Between shafts 31, 31 'of the intermediate degree of freedom 30 is rotatably arranged.
  • the second fixed gear 23 meshes with a second idler gear 25, which is also arranged coaxially to the intermediate shafts 31, 31 'of the intermediate degree of freedom 30 rotatably.
  • the second input shaft 21, the fixed wheels 22, 23 and the idler gears 24, 25 are elements of the second input 20th
  • a switching arrangement A can optionally the fifth idler gear 38 'or the sixth idler gear 39' of the intermediate degree of freedom 30 rotatably connected to the first input shaft 1 1 or switched so that none of the two idler gears 38 ', 39' with the first input shaft 1 1 connected is.
  • the switching arrangement A and the fifth idler gear 38 ' are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the sixth idler gear 39' and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30th
  • the third idler gear 36 of the intermediate degree of freedom 30 or the fourth idler gear 37 of the intermediate degree of freedom 30 can optionally be connected to the second input shaft 21 via a second shift arrangement B. Further, the second switching arrangement B is switchable such that neither the third idler gear 36 nor the fourth idler gear 37 of the intermediate degree of freedom 30 is drive-connected to the second input shaft 21.
  • the third idler gear 36 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 37 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the second connection R between the second input 20 and the intermediate degree of freedom 30.
  • a third switching arrangement C are optionally the first fixed gear 32, and thus the first intermediate shaft 31, the intermediate degree of freedom 30 or the third fixed gear 34 ', and thus the second intermediate shaft 31', the intermediate degree of freedom 30 with the output shaft 41st rotatably connected.
  • the first fixed gear 32 and the third shifting arrangement C form part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the third fixed gear 34 'and the third shifting arrangement C form part of the second connection X2 between the intermediate degree of freedom 30 and the output 40.
  • either the first idler gear 24 or the second idler gear 25 of the second input 20 can be connected to the output shaft 41.
  • the first idler gear 24 of the second input 20 and the fourth shifting arrangement D are elements of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 of the second input 20 and the fourth switching arrangement D are elements of the second connection VI between the second input 20 and the output 40th
  • the first input 10 of the sixth embodiment according to FIG. 8 comprises a first input shaft 11, which can be drive-connected via a first clutch C1 to a drive motor (not shown), as a rule an internal combustion engine of a motor vehicle.
  • the first clutch C1 is designed as a friction clutch, wherein to simplify the present schematic illustration, the first clutch C1 is shown only with a first coupling element, which is part of the first input 10.
  • the intermediate degree of freedom 30 comprises an intermediate shaft 31, which carries four fixed wheels, namely a second fixed gear 33, a third fixed gear 34 ', a fourth fixed gear 38 and a fifth fixed gear 39.
  • a first idler gear 34 is rotatably mounted.
  • the fourth fixed gear 38 meshes with a fifth idler gear 38 'which is rotatably disposed about the first input shaft 1 1.
  • the fifth fixed gear 39 meshes with a sixth idler gear 39 ', which is arranged rotatably about the first input shaft 1 1.
  • the first idler gear 34 meshes with a second idler gear 35 and the third fixed gear 34 'with a third idler gear 36.
  • the second idler gear 35 and the third idler gear 36 are rotatably connected to each other and are arranged together in rotation parallel to the intermediate shaft 31.
  • the second fixed gear 33 is drivingly connected to the intermediate shaft 31 via a wheel, not shown, with a fourth idler gear 37, which is arranged to be rotatable coaxially with the idler gears 35, 36.
  • the second input 20 includes a second input shaft 21, which is arranged coaxially with the first input shaft 1 1 and which is connectable via a second clutch C2 with the drive motor, not shown here.
  • a second clutch C2 with the drive motor, not shown here.
  • only one switching element of the second clutch C2 is shown, wherein the second clutch C2 is designed as a friction clutch.
  • the illustrated switching element of the second clutch C2 is also part of the second input 20.
  • the first fixed gear 22 meshes with a first idler gear 24, which coaxial with the intermediate shaft 31 of the intermediate degree of freedom 30 is rotatably arranged.
  • the second fixed gear 23 meshes with a second idler gear 25 which is also rotatably arranged coaxially with the intermediate shaft 31 of the intermediate degree of freedom 30.
  • the second input shaft 21, the fixed gears 22, 23 and the idler gears 24, 25 are elements of the second input 20.
  • an output shaft 41 is rotatably mounted, which is rotatably connected to an output gear 42, which with a drive assembly for driving wheels of a motor vehicle is connectable, in particular with a differential gear.
  • a switching arrangement A can optionally the fifth idler gear 38 'or the sixth idler gear 39' of the intermediate degree of freedom 30 rotatably connected to the first input shaft 1 1 or switched so that none of the two idler gears 38 ', 39' with the first input shaft 1 1 connected is.
  • the switching arrangement A and the fifth idler gear 38 'of the intermediate degree of freedom 30 are part of the first connection 11 between the first input 10 and the intermediate degree of freedom 30.
  • the sixth idler gear 39' of the intermediate degree of freedom 30 and the switching arrangement A are part of the second connection 12 between the first input 10 and the intermediate degree of freedom 30.
  • a second switching arrangement B is optionally the third idler gear 36 of the intermediate degree of freedom 30 or the fourth idler gear 37 of the intermediate degree of freedom 30 with the second input shaft 21 connectable. Further, the second switching arrangement B is switchable such that neither the third idler gear 36 nor the fourth idler gear 37 of the intermediate degree of freedom 30 is drive-connected to the second input shaft 21.
  • the third idler gear 36 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the first connection 111 between the second input 20 and the intermediate degree of freedom 30.
  • the fourth idler gear 37 of the intermediate degree of freedom 30 and the second switching arrangement B are part of the second connection R between see the second Input 20 and the intermediate degree of freedom 30.
  • either the first idler gear 34 of the intermediate degree of freedom 30 or the third fixed gear 34 'of the intermediate degree of freedom 30 can be connected in a rotationally fixed manner to the output shaft 41.
  • neither the first idler gear 34 nor the third fixed gear 34 ' is connected to the output shaft 41.
  • the first idler gear 34 of the intermediate degree of freedom 30 and the third shifting arrangement C form part of the first connection X1 between the intermediate degree of freedom 30 and the output 40.
  • the third fixed wheel 34 'of the intermediate degree of freedom 30 and the third shifting arrangement C form part of the second connection X2 between the intermediate degree of freedom 30 and the output 40.
  • either the first idler gear 24 or the second idler gear 25 of the second input 20 can be connected to the output shaft 41.
  • the first idler gear 24 of the second input 20 and the fourth shifting arrangement D are elements of the first connection II between the second input 20 and the output 40.
  • the second idler gear 25 of the second input 20 and the fourth switching arrangement D are elements of the second connection VI between the second input 20 and the output 40th

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 pour des véhicules automobiles, avec laquelle il est possible de passer plusieurs vitesses. Cette boîte de vitesses présente quatre degrés de liberté, un des degrés de liberté étant une première entrée (10), un des degrés de liberté étant une seconde entrée (20), un des degrés de liberté étant une sortie (40) et un des degrés de liberté étant un degré de liberté intermédiaire (30). Elle présente également au moins deux liaisons à possibilité de changement de vitesse (11, 12) pouvant être utilisées pour les rapports avant entre la première entrée (10) et le degré de liberté intermédiaire (30), au moins deux liaisons à possibilité de changement de vitesse (X1, X2) pouvant être utilisées pour des rapports avant entre le degré de liberté intermédiaire (30) et la sortie (40), au moins deux liaisons à possibilité de changement de vitesse (II, VI) pouvant être utilisées pour des rapports avant entre la seconde entrée (20) et la sortie (40), et au moins une liaison à possibilité de changement de vitesse (111, R) pour un rapport avant entre la seconde entrée (20) et le degré de liberté intermédiaire (30).
PCT/EP2013/057611 2013-04-11 2013-04-11 Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses WO2014166541A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112013006942.3T DE112013006942A5 (de) 2013-04-11 2013-04-11 Getriebe und Verfahren zum Betreiben eines Getriebes
PCT/EP2013/057611 WO2014166541A1 (fr) 2013-04-11 2013-04-11 Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses
CN201380075507.7A CN105102858B (zh) 2013-04-11 2013-04-11 变速器以及用于运行变速器的方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2013/057611 WO2014166541A1 (fr) 2013-04-11 2013-04-11 Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses

Publications (1)

Publication Number Publication Date
WO2014166541A1 true WO2014166541A1 (fr) 2014-10-16

Family

ID=48236875

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/057611 WO2014166541A1 (fr) 2013-04-11 2013-04-11 Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses

Country Status (3)

Country Link
CN (1) CN105102858B (fr)
DE (1) DE112013006942A5 (fr)
WO (1) WO2014166541A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUA20162178A1 (it) * 2016-03-31 2017-10-01 Antonio Potignano Cambio a doppia frizione
WO2017168305A1 (fr) * 2016-03-31 2017-10-05 Potignano Antonio Transmission manuelle automatique et procédé de fonctionnement
DE102020116544A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116543A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116545A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116540A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116539A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116538A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116542A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116541A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108036028B (zh) * 2017-11-09 2019-10-29 宁波上中下自动变速器有限公司 一种双离合变速器的传动装置及双离合变速器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4658663A (en) * 1984-03-30 1987-04-21 Nissan Motor Co., Ltd. Synchromesh transmission suited for use as automotive automatic transmission
DE10015336A1 (de) 2000-03-28 2001-10-04 Volkswagen Ag Doppelkupplungsgetriebe bzw. Verfahren zur Steuerung eines Doppelkupplungsgetriebes
DE10225331A1 (de) * 2001-07-15 2003-12-24 Richard Boisch Lastschaltgetriebe mit Zentralsynchronisiertung
DE102009020550A1 (de) * 2009-05-06 2010-11-11 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Lastschaltbares Doppelkupplungsgetriebe
DE102011050083A1 (de) 2011-05-04 2012-11-08 Fev Gmbh Getriebe
DE102011083700A1 (de) * 2011-09-29 2013-04-04 Zf Friedrichshafen Ag Kraftfahrzeuggetriebe

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051989A1 (de) * 2008-10-16 2010-04-22 Daimler Ag Doppelkupplungsgetriebe mit zwei Abtriebskonstanten
DE102009020792B4 (de) * 2009-05-07 2020-04-23 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Lastschaltbares Doppelkupplungsgetriebe
DE102010007639A1 (de) * 2010-02-05 2011-08-11 Dr. Ing. h.c. F. Porsche Aktiengesellschaft, 70435 Doppelkupplungsgetriebe
CN102352913B (zh) * 2011-09-30 2015-03-11 长城汽车股份有限公司 多挡位纵置双离合变速器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4658663A (en) * 1984-03-30 1987-04-21 Nissan Motor Co., Ltd. Synchromesh transmission suited for use as automotive automatic transmission
DE10015336A1 (de) 2000-03-28 2001-10-04 Volkswagen Ag Doppelkupplungsgetriebe bzw. Verfahren zur Steuerung eines Doppelkupplungsgetriebes
DE10225331A1 (de) * 2001-07-15 2003-12-24 Richard Boisch Lastschaltgetriebe mit Zentralsynchronisiertung
DE102009020550A1 (de) * 2009-05-06 2010-11-11 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Lastschaltbares Doppelkupplungsgetriebe
DE102011050083A1 (de) 2011-05-04 2012-11-08 Fev Gmbh Getriebe
DE102011083700A1 (de) * 2011-09-29 2013-04-04 Zf Friedrichshafen Ag Kraftfahrzeuggetriebe

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUA20162178A1 (it) * 2016-03-31 2017-10-01 Antonio Potignano Cambio a doppia frizione
WO2017168305A1 (fr) * 2016-03-31 2017-10-05 Potignano Antonio Transmission manuelle automatique et procédé de fonctionnement
DE102020116544A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116543A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116545A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116540A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116539A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116538A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116542A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116541A1 (de) 2020-06-23 2021-12-23 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes
DE102020116540B4 (de) 2020-06-23 2023-05-04 Audi Aktiengesellschaft Fahrzeuggetriebe für eine Antriebseinrichtung eines Kraftfahrzeugs, entsprechende Antriebseinrichtung sowie Verfahren zum Betreiben eines Fahrzeuggetriebes

Also Published As

Publication number Publication date
DE112013006942A5 (de) 2016-01-07
CN105102858B (zh) 2018-12-11
CN105102858A (zh) 2015-11-25

Similar Documents

Publication Publication Date Title
EP2681464B1 (fr) Transmission à double embrayage
WO2014166541A1 (fr) Boîte de vitesses et procédé permettant de faire fonctionner la boîte de vitesses
DE102013215114B4 (de) Hybridantrieb eines Kraftfahrzeugs
EP2742258B1 (fr) Transmission de véhicule automobile
EP2738030A2 (fr) Engrenage à plusieurs groupes assisté en traction et procédé pour le faire fonctionner
EP1972481A1 (fr) Procédé de commande d'un système d'entraînement hybride et système d'entraînement hybride doté de deux boites de vitesses duales
WO2008058858A1 (fr) Boîte de vitesses à engrenages à double embrayage
EP2794317B1 (fr) Entraînement hybride d'un véhicule automobile et son procédé de fonctionnement
DE102010061827A1 (de) Antriebsstrang und Verfahren zum Betreiben desselben
DE102010007639A1 (de) Doppelkupplungsgetriebe
WO2013087944A1 (fr) Transmission pour un véhicule automobile et procédé de commande d'une telle transmission
WO2017186427A1 (fr) Boîte de vitesses à double embrayage à transmission intermédiaire
DE102013209637A1 (de) Parallelschaltgetriebe mit zwei Schaltwalzen und gemischtzahligen Gängen auf den Teilgetriebewellen
DE102011000151A1 (de) Getriebe für ein Kraftfahrzeug und Verfahren zum Steuern eines solchen Getriebes
DE102011084037A1 (de) Kraftfahrzeuggetriebe
DE102010008101A1 (de) Doppelkupplungsgetriebe
DE102011050083A1 (de) Getriebe
DE102018200879A1 (de) Kraftfahrzeuggetriebe
DE102015221780A1 (de) Getriebeanordnung
DE102011005029A1 (de) Doppelkupplungsgetriebe
DE102011000152A1 (de) Getriebe für ein Kraftfahrzeug und Verfahren zum Steuern eines solchen Getriebes
DE102011083695A1 (de) Kraftfahrzeuggetriebe
DE102011005030A1 (de) Doppelkupplungsgetriebe
DE102010022752A1 (de) Antriebsstrang eines Fahrzeuges
DE102015221583A1 (de) Getriebe

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201380075507.7

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13719759

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 1120130069423

Country of ref document: DE

Ref document number: 112013006942

Country of ref document: DE

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112013006942

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13719759

Country of ref document: EP

Kind code of ref document: A1