[go: up one dir, main page]

WO2014114560A1 - Transmission à double embrayage - Google Patents

Transmission à double embrayage Download PDF

Info

Publication number
WO2014114560A1
WO2014114560A1 PCT/EP2014/050851 EP2014050851W WO2014114560A1 WO 2014114560 A1 WO2014114560 A1 WO 2014114560A1 EP 2014050851 W EP2014050851 W EP 2014050851W WO 2014114560 A1 WO2014114560 A1 WO 2014114560A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
countershaft
drive
electric machine
dual
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2014/050851
Other languages
German (de)
English (en)
Inventor
Raphael Biancale
Roland HINTRINGER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Original Assignee
AVL List 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 AVL List GmbH filed Critical AVL List GmbH
Publication of WO2014114560A1 publication Critical patent/WO2014114560A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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 parallel flow paths, e.g. dual clutch transmissions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • 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
    • F16H3/12—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 means for synchronisation not incorporated in the clutches
    • F16H3/126—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 means for synchronisation not incorporated in the clutches using an electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0441—Arrangements of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0446—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control the supply forming part of the transmission control unit, e.g. for automatic transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears 
    • F16H57/0494—Gearings with spur or bevel gears  with variable gear ratio or for reversing rotary motion
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4816—Electric machine connected or connectable to gearbox internal 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions
    • F16H2003/008—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions comprising means for selectively driving 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more 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
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0095—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising four reverse 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the invention relates to a dual-clutch transmission, in particular for a motor vehicle, having an input shaft and a main shaft, wherein the input shaft via a switchable first clutch with a first countershaft and a switchable second clutch with a second countershaft is connectable, wherein the first countershaft and the second countershaft
  • the countershaft can be drive-connected to the main shaft via at least one pair of gearshifting gears via a shifting device, with at least one synchronizing device, which is formed by an electric machine, for adjusting the speed of the countershafts to the main shaft.
  • the object of the invention is to avoid these disadvantages and to propose a space and part-saving pressure source for hydraulic devices, in particular system pressure and / or lubricating oil systems.
  • the electric machine is drive-connected to a hydraulic pump, wherein preferably a drive shaft of the electric machine and a drive shaft of the hydraulic pump, preferably a system pressure and / or lubricating oil pump, are arranged coaxially.
  • a hydraulic pump wherein preferably a drive shaft of the electric machine and a drive shaft of the hydraulic pump, preferably a system pressure and / or lubricating oil pump, are arranged coaxially.
  • the electric machine is thus designed as a multifunctional component and can be used for synchronization of the countershafts, as a drive for the hydraulic pump, or for hybrid functions, such as providing drive or braking torque, in particular for recuperation, as well as a starter motor for the internal combustion engine.
  • a drive for the hydraulic pump or for hybrid functions, such as providing drive or braking torque, in particular for recuperation, as well as a starter motor for the internal combustion engine.
  • a dog clutch clutch - Preferably designed as a dog clutch clutch -, particularly preferably via at least one gear stage, is drive-connected with the first or second countershaft.
  • the electric machine by means of a single clutch, preferably a dog clutch, either via a first gear stage with the first countershaft or via a second gear stage with the second countershaft are drivingly connected.
  • the electric machine can be connected to either the first or the second countershaft, or separated from both. As a result, the electric machine can ensure the drive for the lubricating oil pump even when the vehicle is at a standstill.
  • a single electric machine via a first gear stage and a first clutch to the first countershaft and via a second gear stage and a second clutch to the second countershaft is drive-connected.
  • This design is characterized by very few components.
  • a second embodiment of the invention provides that the first countershaft a first electric machine and the second countershaft is assigned a second electric machine.
  • the first electric machine is drive-connected via a first clutch, preferably a dog clutch, and at least a first gear stage with the first countershaft. It when the first electric machine via the first clutch and a further first gear stage with the first clutch is particularly advantageous
  • first clutch - Preferably with an input shaft side part of the first clutch - is drive connectable. This makes it possible to connect the first electric machine-bypassing the first countershaft-to the input shaft and thus directly to the internal combustion engine, for example for starting the internal combustion engine, or for charging the vehicle battery via the internal combustion engine when the vehicle is stationary.
  • the second electric machine via a second clutch, preferably a dog clutch, and at least one - - Second gear stage with the second countershaft and via the second clutch and a further second gear stage with the second clutch - preferably with an input shaft side part of the second clutch - is drive-connected.
  • a second clutch preferably a dog clutch
  • the first or second gear stage and the further first or second gear stages may optionally have different ratios.
  • the first and the second clutch of the double clutch are advantageously designed as wet-running Lammellenkupplungen, whereby high torques are transferable with a small space and low weight.
  • the two clutches can be designed identical, in order to minimize the manufacturing costs.
  • the switching devices are formed by jaw clutches.
  • the switching devices themselves can be made unsynchronized.
  • At least one gear group of the first countershaft and the second countershaft is of identical construction. By using as many common parts as possible, the costs can be kept very low.
  • a range group transmission is connected to the main shaft, wherein preferably the range group transmission comprises a planetary gear.
  • the range group transmission comprises a planetary gear.
  • the input shaft is connected via a first gear stage to the first countershaft and via a second gear stage to the second countershaft, wherein preferably the first and the second gear stage have different gear ratios. Due to the different gear ratios, the countershafts are driven at different speeds.
  • the ratio jump between the first and second gear stage corresponds to the desired ratio jump between the individual gear ratios, as a result of which - - Training of the gear groups on the two countershafts is possible.
  • the input shaft with the main shaft directly via a dog clutch with or without synchronization is connectable.
  • the actuation of the dog clutches can be done via hydraulically actuated actuators.
  • the drive shaft of the electric machine is connected to the drive shaft of the pump via a planetary gear, preferably the drive shaft with a sun gear of the planetary gear and the drive shaft is rotatably connected to a web shaft of the planetary gear.
  • FIGS. show schematically:
  • Fig. 1 shows an inventive dual-clutch transmission in a first
  • Fig. 2 shows an inventive dual-clutch transmission in a second
  • Fig. 3 shows an inventive dual-clutch transmission in a third
  • Fig. 4 shows an inventive dual-clutch transmission in a fourth
  • the figures each show an inventive dual-clutch transmission 10 with twelve forward gears and four reverse gears.
  • the different gear ratios are shown in FIG. designated by the reference numerals 1, 2, 3, 4, 5, 6 for the forward gears and Rl, R2 for the reverse gears.
  • the in each of the Fig. illustrated dual-clutch transmission 10 has an input shaft 11 connected to an internal combustion engine, not shown, and a main shaft 13 connected to an output shaft 12.
  • the input shaft 11 is connected via single-stage first and second input gear stages 14, 15, which have different gear ratios, each with a A first countershaft 16 and a second countershaft 17 are connected.
  • a first shiftable clutch 18, between the second input gear stage 15 and the second countershaft 17, a switchable second clutch 19 is arranged between the first input gear stage 14 and the first countershaft 16, a first shiftable clutch 18, between the second input gear stage 15 and the second countershaft 17, a switchable second clutch 19 is arranged.
  • the clutches 18 and 19 are designed as wet-running multi-plate clutches.
  • the first and second clutches 18, 19 may be spring loaded in the closed position, whereby no active force application is required to drive connection between the input shaft
  • range group transmission 21 In the drive train of the dual-clutch transmission 10 is further connected to the main shaft 13 range group transmission 21 is provided, with which switching between high gear ratios - fast range group HIGH - and low gear ratios - slow range group LOW - is possible.
  • the range group transmission 21 can be formed from two gear pairs with different gear ratios, each with a fixed gear and a loose gear between which can be switched by a switching device 20.
  • the range group transmission 21 may be formed as a planetary gear 24, wherein an element of the planetary gear 24 may be held by a switching device 20 or connected to a second element of the planetary gear 24.
  • Reference numeral 25 in Fig. 2 is one with the main shaft 13 or output shaft
  • the countershafts 16, 17 are in each case via gear stages ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 with the main shaft 13 in connection.
  • the gears of the gear stages ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZA7 ZR1, ZR2, the gear stages 14, 15 and the range group transmission 21 are zl, z2, z3, z4, z5, z6, z7, z8, z9, zlO, zl l, zl2, zl3, zl4, zl5, zl6, zl7, zl8 denoted, wherein identical gears are provided with the same reference numerals.
  • Each gear stage ZA1, ZA2, ZA3, ZA4, ZA5, ZA6, ZR1, ZR2 each have at least one free on a shaft - for example, a countershaft 16, 17 - circulating gear and one with another shaft - for example, the main shaft 13 - rotatably connected gear on.
  • the gear stages ZR1, ZR2 the reverse gears Rl, R2 additionally have a reverse gear zl2. In order to save manufacturing costs, two each on the countershafts 16, - -
  • the 17 opposing gears may be formed as equal parts.
  • the gears can be mounted on the countershafts 16, 17 freewheeling and are rotatably connected to the main shaft 13 gears in the tooth-engaging.
  • switching elements 20 are provided, which can be formed by synchronizing or - especially in the case of external electric or hydraulic synchronizers - by simple, non-synchronized jaw clutches.
  • the switching elements 20 can be actuated by not shown actuators, for example hydraulically.
  • the drive-connected countershaft for example, the second countershaft 17 is drivingly connected to the main shaft 13 via an engaged gear, such as gear 6.
  • the main shaft 13 is drivingly connected via the switched to HIGH or LOW switching device 20 of the range group transmission 21 to the output shaft 12 and a switched gear, such as gear 6, with the second countershaft 17.
  • a power flow up to the output shaft 12 takes place via the second clutch 19.
  • the input shaft 11 is connected to the main shaft 13 directly via a coupling 40. Thereby, a direct drive between the input shaft 11 and the main shaft 13 are made possible.
  • the dual-clutch transmission 10 may have a modular design and consist of a coupling part 50, a main transmission part 60 and the range group transmission part 70, and thus for different applications and vehicles, such as buses, trucks, road vehicles and off-road vehicles application.
  • the modular design also allows application and upgrading of existing gearboxes. Thus, a use in the most common dual-clutch transmissions with range group is possible.
  • synchronizers 80 formed by electric machines 81, 181, 281 are provided, each having at least one claw coupling - -
  • Clutch 82, 83 and at least one gear stage 84, 85, 84a, 85a, with the first or second countershaft 16, 17 is drive-connected.
  • the drive shaft 81a, 181a, 281a of the electric machine 81, 181, 281 is drive-connected to the drive shaft 86a, 186a, 286a of a pump 86, 186, 286, for example a lubricating oil pump.
  • the electrical machines 81, 181, 281 can be operated both by motor and by generator.
  • the electrical machines 81, 181, 281 are designed as multifunctional components and serve to synchronize the countershafts 16, 17 during switching operations, to drive the pump 86, 186, 286, to start the internal combustion engine, to charge the vehicle battery and take over hybrid functions such as providing Drive and braking torque, as well as for recuperation.
  • a single electric machine 81 is provided, which is fixedly connected drive-connected with a pump 86.
  • the shafts 81a, 86a can be brought into drive connection with either the first countershaft 16 or the second countershaft 17 via the first and second clutches 82, 83 and the first gear stage 84 and second gear stage 85, respectively.
  • the electric machine 81 can be used as a central synchronization device for the countershafts 16, 17 during gear change operations.
  • hybrid functions can also be taken over by the electric machine 81, such as providing additional drive or braking torque.
  • the electric machine 81 can also be used for starting the internal combustion engine or - operated as a generator - for charging the vehicle battery.
  • both the first and the second clutch 82, 83 are deactivated, the pump 86 - regardless of the speed of the countershafts 16, 17 - driven by the electric machine 81, whereby a sufficient lubricating oil supply can also be done when the vehicle is stationary.
  • the electric machine 81 is fixedly connected to the pump 86, whereby the required lubricating oil pressure is ensured.
  • each countershaft 16, 17 is associated with an electric machine 181, 281, wherein the drive shaft 181a of the first electric machine 181 with a drive shaft 186a of a first pump 186, and the drive shaft 281a of the second electric machine 281 with a drive shaft 286a a second pump 286 drivingly connected.
  • the common shaft 181a / 186a of the first electric machine 181 can be connected via the first clutch 82 to a first gear stage 84 or to a further first gear stage 84a.
  • the first gear 84 is connected directly to the first countershaft 16.
  • the further first gear stage 84a is connected to a coupling part 18a of - First clutch 18 is connected, which is drivingly connected via the first input gear stage 14 to the input shaft 11.
  • the common shaft 281a / 286a of the second electric machine 281 can be connected via the second clutch 83 to a second gear stage 85 or to a further second gear stage 85a.
  • the second gear 85 is in turn connected directly to the second countershaft 17.
  • the further second gear stage 85a is connected to a coupling part 19a of the second clutch 19, which is drive-connected via the second input gear stage 15 to the input shaft 11.
  • each of the two electric machines 181, 281 can be selectively connected to the respective countershaft 16, 17 or to the input shaft 16, a larger number of operating modes can be realized than in the first embodiment variant. If, for example, one of the electrical machines 181, 281 is connected to the respective coupling part 18a, 19a, the internal combustion engine can be started directly - with the countershafts 16, 17 stationary. On the other hand, when the countershafts 16, 17 are stationary with the internal combustion engine, the vehicle battery can be charged directly via the first or second electric machine 181, 281 - or via both electric machines 181, 281.
  • FIG. 3 and FIG. 4 show dual-clutch transmission 10 without range group transmission.
  • each of the drive shaft 86a of the pump 86 is connected via a planetary gear 90 to the drive shaft 81a of the electric machine 81, wherein the drive shaft 81a with the sun gear 90a and the drive shaft 86a of the pump 86 is connected to the ridge shaft 90b of the planetary gear 90.
  • the ring gear 90c of the planetary gear 90 is formed fixed to the housing.
  • the planetary gear 90 is disposed between the electric machine 81 and the first and second gear stages 84, 85.
  • only one clutch 823 is disposed between the electric machine 81 and the pump 86.
  • the clutch 823 between the first and second gear stage 84, 85, and the planetary gear 90 between the first gear stage 84 and the - - positioned electrical machine.
  • About the respective shaft 86a of the pump 86 and the drive shaft 81a firmly connected clutch 823 can - via the respective first and second gear stage 84, 85 - the first and second countershaft 16, 17 rotatably with the shaft 86a and the land shaft 90b get connected.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

L'invention concerne une transmission à double embrayage (10) en particulier pour un véhicule à moteur, comprenant un arbre d'entrée (11) et un arbre principal (13), l'arbre d'entrée (11) pouvant être relié par un premier embrayage (18) débrayable à un premier arbre intermédiaire (16) et par un deuxième embrayage (19) débrayable à un deuxième arbre intermédiaire (17), le premier arbre intermédiaire (16) et le deuxième arbre intermédiaire (17) pouvant être respectivement reliés en entraînement à l'arbre principal (13) par l'intermédiaire d'au moins une paire de roues dentées (Z) débrayable par l'intermédiaire d'un dispositif de changement de vitesses (20), et comprenant au moins un dispositif de synchronisation (80) formé par un moteur électrique (81, 181, 281) pour adapter la vitesse de rotation des arbres intermédiaires (16, 17) à celle de l'arbre principal (13). Pour fournir une source de pression pour les dispositifs hydrauliques ayant un encombrement le plus faible possible et ayant un nombre de pièces le petit possible, le moteur électrique (81, 181, 281) est relié en entraînement à une pompe hydraulique (86, 186, 286), un arbre d'entraînement (81a, 181a, 281a) du moteur électrique (81, 181, 281) et un arbre moteur de la pompe hydraulique (86, 186, 286) étant de préférence disposés de manière coaxiale.
PCT/EP2014/050851 2013-01-22 2014-01-17 Transmission à double embrayage Ceased WO2014114560A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50038/2013 2013-01-22
ATA50038/2013A AT513388B1 (de) 2013-01-22 2013-01-22 Doppelkupplungsgetriebe

Publications (1)

Publication Number Publication Date
WO2014114560A1 true WO2014114560A1 (fr) 2014-07-31

Family

ID=49998271

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/050851 Ceased WO2014114560A1 (fr) 2013-01-22 2014-01-17 Transmission à double embrayage

Country Status (2)

Country Link
AT (1) AT513388B1 (fr)
WO (1) WO2014114560A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015200067A1 (de) * 2014-01-08 2015-07-09 Volkswagen Aktiengesellschaft Hybridantriebsanordnung eines Kraftfahrzeuges und Verfahren zu ihrer Steuerung und/oder Regelung
CN108105342A (zh) * 2016-11-24 2018-06-01 格特拉克·福特传动系统有限公司 带有油泵的换挡变速器
CN110116615A (zh) * 2019-05-28 2019-08-13 青岛大学 一种重型商用汽车用并联混合动力变速器
CN110864109A (zh) * 2018-08-27 2020-03-06 腓特烈斯港齿轮工厂股份公司 用于双离合器变速器的液压系统
US11820523B1 (en) 2022-10-06 2023-11-21 Archer Aviation, Inc. Systems and methods for, and components of, gearboxes for eVTOL aircraft
US12227300B2 (en) 2022-10-06 2025-02-18 Archer Aviation Inc. Systems and methods for oil maintenance in gearboxes for eVTOL aircraft
US12234021B2 (en) 2022-10-06 2025-02-25 Archer Aviation Inc. Systems and methods for improved gearboxes for evtol aircraft

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019209931B4 (de) * 2019-07-05 2024-11-21 Zf Friedrichshafen Ag Lastschaltbares Hybridgetriebe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19850549A1 (de) * 1998-11-03 2000-05-04 Bosch Gmbh Robert Getriebe für ein Kraftfahrzeug, insbesondere Doppelkupplungs-Schaltgetriebe, und Verfahren zum Betreiben des Getriebes
DE10133695A1 (de) * 2000-07-18 2002-03-07 Luk Lamellen & Kupplungsbau Getriebe
EP1610038A1 (fr) * 2004-06-21 2005-12-28 Getrag Ford Transmissions GmbH Transmission avec accouplement double
DE102006054281A1 (de) * 2006-11-17 2008-06-12 Zf Friedrichshafen Ag Doppelkupplungs-Windungsgetriebe
WO2012168116A1 (fr) * 2011-06-09 2012-12-13 Avl List Gmbh Transmission à double embrayage pour véhicule à moteur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7086977B2 (en) * 2001-05-03 2006-08-08 Ford Global Technologies, Llc Transmission arrangements for hybrid electric vehicles

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19850549A1 (de) * 1998-11-03 2000-05-04 Bosch Gmbh Robert Getriebe für ein Kraftfahrzeug, insbesondere Doppelkupplungs-Schaltgetriebe, und Verfahren zum Betreiben des Getriebes
DE10133695A1 (de) * 2000-07-18 2002-03-07 Luk Lamellen & Kupplungsbau Getriebe
EP1610038A1 (fr) * 2004-06-21 2005-12-28 Getrag Ford Transmissions GmbH Transmission avec accouplement double
DE102006054281A1 (de) * 2006-11-17 2008-06-12 Zf Friedrichshafen Ag Doppelkupplungs-Windungsgetriebe
WO2012168116A1 (fr) * 2011-06-09 2012-12-13 Avl List Gmbh Transmission à double embrayage pour véhicule à moteur

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015200067A1 (de) * 2014-01-08 2015-07-09 Volkswagen Aktiengesellschaft Hybridantriebsanordnung eines Kraftfahrzeuges und Verfahren zu ihrer Steuerung und/oder Regelung
CN108105342A (zh) * 2016-11-24 2018-06-01 格特拉克·福特传动系统有限公司 带有油泵的换挡变速器
CN108105342B (zh) * 2016-11-24 2019-06-14 格特拉克·福特传动系统有限公司 带有油泵的换挡变速器
CN110864109A (zh) * 2018-08-27 2020-03-06 腓特烈斯港齿轮工厂股份公司 用于双离合器变速器的液压系统
CN110116615B (zh) * 2019-05-28 2023-12-29 青岛大学 一种重型商用汽车用并联混合动力变速器
CN110116615A (zh) * 2019-05-28 2019-08-13 青岛大学 一种重型商用汽车用并联混合动力变速器
US12024304B2 (en) 2022-10-06 2024-07-02 Archer Aviation, Inc. Systems and methods for oil maintenance in gearboxes for eVTOL aircraft
US12208908B2 (en) 2022-10-06 2025-01-28 Archer Aviation Inc. Systems and methods for oil management in gearboxes for eVTOL aircraft
US11958621B1 (en) 2022-10-06 2024-04-16 Archer Aviation, Inc. Systems and methods for, and components of, gearboxes for eVTOL aircraft
US11975853B2 (en) 2022-10-06 2024-05-07 Archer Aviation, Inc. Systems for cooling an electrical engine for eVTOL aircraft using an end bell assembly connected to a thermal plate
US11820523B1 (en) 2022-10-06 2023-11-21 Archer Aviation, Inc. Systems and methods for, and components of, gearboxes for eVTOL aircraft
US12030656B1 (en) 2022-10-06 2024-07-09 Archer Aviation, Inc. Systems and methods for oil management in gearboxes for evtol aircraft
US12129040B2 (en) 2022-10-06 2024-10-29 Archer Aviation Inc. Systems and methods for oil management in gearboxes for eVTOL aircraft
US11912424B1 (en) 2022-10-06 2024-02-27 Archer Aviation Inc. Systems and methods for improved gearboxes for eVTOL aircraft
US12227300B2 (en) 2022-10-06 2025-02-18 Archer Aviation Inc. Systems and methods for oil maintenance in gearboxes for eVTOL aircraft
US12234021B2 (en) 2022-10-06 2025-02-25 Archer Aviation Inc. Systems and methods for improved gearboxes for evtol aircraft
US12286234B2 (en) 2022-10-06 2025-04-29 Archer Aviation Inc. Aircraft electric propulsion system with overlapping shafts for gearbox oil distribution
US12312091B2 (en) 2022-10-06 2025-05-27 Archer Aviation Inc. Systems and methods for improved gearboxes for evtol aircraft
US12384547B2 (en) 2022-10-06 2025-08-12 Archer Aviation Inc. Systems and methods for improved gearboxes for EVTOL aircraft
US12473074B2 (en) 2022-10-06 2025-11-18 Archer Aviation Inc. Aircraft propulsion system including pump gear driven by planetary gearbox assembly
US12486021B2 (en) 2022-10-06 2025-12-02 Archer Aviation Inc. Electric propulsion system for an aircraft including a motor located between a gearbox assembly and a propeller
US12486022B2 (en) 2022-10-06 2025-12-02 Archer Aviation Inc. Systems and methods for oil management in gearboxes for EVTOL aircraft

Also Published As

Publication number Publication date
AT513388B1 (de) 2014-04-15
AT513388A4 (de) 2014-04-15

Similar Documents

Publication Publication Date Title
AT513388B1 (de) Doppelkupplungsgetriebe
DE102010008754B4 (de) Antriebssystem, insbesondere für ein Kraftfahrzeug
EP2886383B1 (fr) Chaîne cinématique hybride pour un véhicule automobile
EP1937501B1 (fr) Boite de vitesses a double embrayage pour un vehicule automobile, en particulier equipe d'un systeme de propulsion hybride, et procede de commande de cette boite de vitesses a double embrayage
DE102005049992B4 (de) Verfahren zum Steuern eines Antriebsstranges
EP3004688B1 (fr) Boîte de vitesses à double embrayage pour véhicule automobile
EP2450215B1 (fr) Engrenage hybride
DE102016221097A1 (de) Drehmomentübertragungsvorrichtung für Hybridantriebe
DE102011113288B4 (de) Kfz-Antriebsstrang und Verfahren zum Betreiben eines Antriebsstranges
DE102015205932A1 (de) Elektrifizierbare Drehmomentübertragungsvorrichtung
AT510966B1 (de) Getriebe, insbesondere doppelkupplungsgetriebe
DE102021213669B4 (de) Schleppverlustarmes Hybridgetriebe in Mischbauweise
DE102022106552A1 (de) Hybridgetriebe sowie Antriebsstrang mit Hybridgetriebe
AT520555B1 (de) Antriebsstrang für ein kraftfahrzeug
AT512917B1 (de) Verfahren zum Betreiben eines Doppelkupplungsgetriebes
DE102015121157A1 (de) Hybrid-Antriebsstrang
DE10145790A1 (de) Kurzbauende Lastschaltgetriebe
DE102014019431A1 (de) Hybridantrieb für ein Fahrzeug
DE102022203688A1 (de) Kompaktes Hybridgetriebe
DE102022202920B4 (de) Hybridgetriebe
DE102022202924B4 (de) Hybridgetriebe
DE102021205343B4 (de) Lastschaltbares Hybridgetriebe
DE102022206202B4 (de) Kompakter Hybrid-Antriebsstrang
DE102022202926B4 (de) Kompaktes Dreigang-Hybridgetriebe
DE102021213652B4 (de) Viergang-Hybridgetriebe

Legal Events

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

Ref document number: 14700883

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14700883

Country of ref document: EP

Kind code of ref document: A1