WO2020160865A1 - Transmission device for a motor vehicle - Google Patents

Transmission device for a motor vehicle Download PDF

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Publication number
WO2020160865A1
WO2020160865A1 PCT/EP2020/050355 EP2020050355W WO2020160865A1 WO 2020160865 A1 WO2020160865 A1 WO 2020160865A1 EP 2020050355 W EP2020050355 W EP 2020050355W WO 2020160865 A1 WO2020160865 A1 WO 2020160865A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
output shaft
transmission device
input shaft
Prior art date
Application number
PCT/EP2020/050355
Other languages
German (de)
French (fr)
Inventor
Christian Meixner
Original Assignee
Audi Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Audi Ag filed Critical Audi Ag
Publication of WO2020160865A1 publication Critical patent/WO2020160865A1/en

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Classifications

    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • 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
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3462—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear with means for changing distribution of torque between front and rear wheels
    • 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
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
    • B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
    • B60K6/52—Driving a plurality of drive axles, e.g. four-wheel drive
    • 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
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • 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
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/356—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having fluid or electric motor, for driving one or more wheels
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
    • B60K2006/4808—Electric machine connected or connectable to gearbox output shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/90—Vehicles comprising electric prime movers
    • B60Y2200/92—Hybrid vehicles
    • 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 transmission device for a motor vehicle, which has an input shaft that can be effectively connected to a drive direction of the motor vehicle, as well as a first output shaft and a second output shaft and has a torque displacement gear designed as a planetary gear, via which the input shaft with the first output shaft and the second Output shaft is coupled.
  • the document EP 1 494 886 B1 is known from the prior art.
  • This relates to a transmission system for a vehicle, the transmission system comprising: a drive shaft which is connected to a differential mechanism which has two output shafts, the two output shafts each carrying first and second coaxially mounted sun gears of a planetary gear, each in first and Engage second planetary gear sets, the gear ratio of the first sun gear with the first planetary gear set differs from that of the second sun gear with the second planetary gear set, each first planet gear being connected to an associated second planet gear so that it is an associated common one Planet shaft rotates, the planet shaft being connected to a common carrier which is rotatably mounted coaxially with the first and second sun gears, a single selectively actuated speed change means which is connected to the carrier and is adapted to the rotational speed of the carrier rs to increase or decrease its axis, wherein the transmission system further comprises at least one sensor which is designed to generate a signal that indicates an operating parameter of the vehicle or its engine, and a
  • the object of the invention is to propose a transmission device for a motor vehicle which has advantages over known transmission devices, in particular realizing a “torque vectoring” functionality between the two output shafts despite an extremely compact design.
  • the planetary gear is a stepped planetary gear, which has a plane carrier on which at least a first planetary gear and a second planetary gear, which is arranged axially to the at least one first planetary gear and connected to it, are rotatably mounted, the first planetary gear being rotatably mounted with a first sun gear and the second planet gear meshes with a second sun gear, wherein the planet carrier is rotatably coupled to the input shaft and the first output shaft and the first sun gear is rotatably coupled to the second output shaft and / or via a reinforcing planetary gear, and wherein the second sun wheel is connected to an electrical machine via a clutch assembly.
  • the transmission device is used to transmit a torque or drive torque between the drive device of the motor vehicle on the one hand and at least one wheel axle of the motor vehicle on the other hand.
  • the at least one wheel axle is operatively connected or at least operatively connected to the drive direction via the transmission device.
  • the at least one wheel axle is accordingly as a driven wheel axle. It can in particular be designed as a front wheel axle or a rear wheel axle of the motor vehicle.
  • the gear unit is used in particular to distribute the drive torque provided by the drive unit to different sub-axles of this wheel axis, with at least one wheel of the motor vehicle being coupled or at least connectable to the gear unit and corresponding to the drive unit via each of the sub-axles.
  • the gear unit serves as an axle differential gear.
  • the gear mechanism serves as a center differential gear to distribute the drive torque to the different wheel axles.
  • the wheel axles are available, for example, as a front wheel axle and a rear wheel axle.
  • the transmission device has the input shaft and the first output shaft and the second output shaft.
  • the input shaft of the gearbox device is connected in terms of drive technology to the drive device of the motor vehicle, preferably via a gearbox and / or a clutch, in particular a starting clutch.
  • a translation selected from several translations between the drive device and the input shaft of the transmission device can be set.
  • the clutch is preferably designed as a shift clutch and particularly preferably as a starting clutch. With the aid of the clutch, the operative connection between the drive device and the input shaft of the transmission device can be optionally established or interrupted.
  • the first output shaft is operatively connectable or operatively connected to a first partial shaft of the wheel axle, in particular via a first gear
  • the second output shaft is operatively connected to a second partial shaft of the wheel axle, in particular via a second gear.
  • the first output shaft is particularly preferably permanent and / or rigid the first partial shaft and the second output shaft permanently and / or rigidly coupled to the second partial shaft.
  • the first output shaft is operatively connectable or operatively connected to a first wheel axle, in particular via the first gear
  • the second output shaft is operatively connected to the second wheel axle, in particular via the second gear.
  • first output shaft is preferably permanently and / or rigidly coupled to the first wheel axle and the second output shaft is permanently and / or rigidly coupled to the second wheel axle.
  • the first gear and the second gear can each be designed as a ring gear, so that the axes of rotation of the two partial shafts or the two wheel axles are angled with respect to the axes of rotation of the output shafts, i.e. they enclose an angle that is greater than 0 ° and less than 180 ° is.
  • the drive direction has at least one drive unit which is designed, for example, as an internal combustion engine or as an electric machine.
  • the drive direction can also be present as a hybrid drive device and in this respect have several drive units, which are preferably of different types.
  • one of the drive units is, for example, an internal combustion engine and another of the drive units is an electrical machine.
  • the drive device has several drive units, it is preferably designed in such a way that the drive units jointly provide the drive torque aimed at driving the motor vehicle, at least temporarily.
  • the input shaft of the transmission device is drive-coupled via the torque displacement gear, which is present as a planetary gear, both to the first output shaft and to the second output shaft, in particular permanently.
  • the coupling of the shafts via the torque displacement gear is in particular torque-dividing, so that the drive torque provided on the input shaft is divided between the first output shaft and the second output shaft.
  • the torque shift gear is a differential gear, which has several rere having intermeshing spur gears. In general, the torque shift gear works as a differential gear or differential gear.
  • the torque shift transmission has two sun gears, namely the first sun gear and the second sun gear.
  • One of the sun gears is coupled to one of the output shafts, namely preferably rigidly and / or permanently.
  • the first sun gear is coupled to the second output shaft.
  • each of the output shafts is decoupled from the other of the output shafts, that is to say, within the scope of the transmission device, it is only connected to it in terms of drive technology via the torque displacement transmission, but in particular not rotationally fixed.
  • the first sun gear which is coupled in a rotationally fixed manner to the second output shaft, is decoupled from the first output shaft.
  • the output shafts are connected to one another away from the transmission device via the wheel axles and a base of the motor vehicle.
  • the torque shift transmission has the planet carrier on which the at least one first planetary gear and the least one second planetary gear are rotatably mounted.
  • the gear device can have exactly one first planetary gear or several first planetary gears.
  • the transmission device can have exactly one second planetary gear or several second planetary gears.
  • the torque shifting gear has as many first planetary gears as there are second planetary gears and vice versa. If the first planetary gear or the second planetary gear is mentioned in the context of this description, the explanations always refer to the at least one first planetary gear or the at least one second planetary gear, unless the contrary is indicated.
  • the two planet gears that is to say the at least one first planet gear and the least one second planet gear, are arranged coaxially to one another and connected to one another in a rotationally fixed manner. That means the planet gears are jointly mounted on the planet carrier, in particular via a common shaft. They always have the same speed with respect to a common axis of rotation. For this they are rigidly and permanently connected to one another.
  • the planetary gear can also be referred to as a stepped planetary gear.
  • the first planetary gear and the second planetary gear can have the same diameter. However, they are preferably designed with different diameters.
  • the first planet gear meshes with the first sun gear and the second planet gear meshes with the second sun gear.
  • the first planet gear meshes exclusively with the first sun gear and the second planet gear exclusively with the second sun gear.
  • the torque shift gear is designed without a ring gear. So there is no ring gear that meshes with the first planet gear or the second planet gear.
  • the planet carrier is rotatably coupled to the input shaft and the first output shaft. This means that, within the framework of the transmission device, the input shaft is rigidly and permanently coupled to the first output shaft, namely via the planetary carrier of the torque displacement transmission.
  • the second output shaft is only connected to the plane carrier via the first sun gear.
  • the first sun gear is permanently coupled to the second output shaft, namely non-rotatably and / or via the reinforcement planetary gear.
  • the non-rotatable coupling there can of course be at least one gear stage between the first sun gear and the second output shaft, provided that this ensures the non-rotatable or rigid connection of the first sun gear to the second output shaft.
  • the planetary gear is designed as a plus planetary gear.
  • the second sun gear is connected to the electrical machine in terms of drive technology via the clutch assembly.
  • the electrical machine can be optionally coupled to the second sun gear.
  • a first Switching setting of the clutch assembly is to the extent that the electric machine is coupled to the second sun gear, preferably rigidly or rotated.
  • the electric machine is decoupled from the second sun gear. If the electric machine is drive-connected to the second sun wheel, the electric machine can be used to split the drive torque applied to the input shaft to the first output shaft and the second output shaft.
  • the electrical machine enables so-called “torque vectoring”.
  • the transmission device is designed to be very compact.
  • a further embodiment of the invention provides that the first planet wheel and the second planet wheel have different diameters from one another. This has already been pointed out.
  • the design of the two planet gears with different diameters enables an excellent distribution of the drive torque applied to the input shaft between the first output shaft and the second output shaft with the aid of the electric machine. Due to the different diameters of the planetary gears, a comparatively small additional torque of the electrical machine is necessary to distribute the drive torque to the output shafts.
  • the electrical machine can have a significantly lower nominal power than the drive device of the motor vehicle.
  • the rated power of the electrical machine is a maximum of 50%, a maximum of 25%. maximum 20%, maximum 15% or maximum 10% of the nominal power of the drive device.
  • a preferred further embodiment of the invention provides that the input shaft is designed as a hollow shaft and the second output shaft extends through the input shaft at least in some areas.
  • the second output shaft is at least partially arranged in the input shaft and passes through it.
  • the second output shaft preferably extends completely through the input shaft, viewed in the axial direction with respect to an axis of rotation of the input shaft.
  • the input shaft and the second output shafts are arranged coaxially to one another.
  • the first output shaft is also particularly preferably arranged coaxially with the input shaft and the second output shaft.
  • the second output shaft is rotatably mounted in and / or on the input shaft.
  • the mounting of the second output shaft on the input shaft is realized, for example, with the aid of a bearing arranged in the input shaft, which engages in the radial direction outside on an inner circumference of the input shaft and in the radial direction inside on an outer circumference of the second output shaft.
  • the bearing is preferably designed as a roller bearing. However, it can also be in the form of a plain bearing. The configuration described enables a compact and space-saving configuration of the transmission device.
  • the second sun gear is connected in terms of drive technology to the clutch arrangement via an intermediate shaft.
  • the intermediate shaft establishes the drive connection between the second sun gear and the clutch arrangement.
  • the second sun gear and the clutch arrangement are preferably rigidly and / or permanently coupled to one another via the septwel le.
  • the intermediate shaft extends out of the planet carrier in the axial direction. The use of the intermediate shaft enables the stepped planetary gear to be connected to the clutch arrangement in a simple manner.
  • a further development of the invention provides that the planet carrier on the one hand is non-rotatably connected to the input shaft and on the other hand to a further intermediate shaft arranged coaxially with the input shaft. Seen in the axial direction, the input shaft and the wide re intermediate shaft attack on opposite sides of the planet carrier.
  • the input shaft and the further intermediate shaft are arranged coaxially to one another, that is to say they have the same axis of rotation.
  • the further intermediate shaft is used, for example, to support the planetary carrier and / or the drive-related connection of the planetary carrier to the clutch arrangement.
  • the intermediate shaft and the further intermediate Intermediate shaft represent output shafts of the clutch assembly and can be coupled to the electrical machine each Weil. As a result, a simple and flexible connection of the electrical machine to the torque displacement gear is realized.
  • the intermediate shaft and / or the further intermediate shaft are designed as a hollow shaft and the first output shaft extends through the intermediate shaft and / or the further intermediate shaft at least in regions.
  • Each of the shafts mentioned, that is to say the intermediate shaft and the further intermediate shaft, can be designed as a hollow shaft.
  • the first output shaft extends through the respective ge shaft preferably completely in the axial direction.
  • the first output shaft is preferably mounted in and / or on the intermediate shaft or the further intermediate shaft.
  • a bearing for example a roller bearing or a plain bearing, is provided for mounting the first output shaft on the respective shaft.
  • Both the intermediate shaft and the further intermediate shaft are particularly preferably in the form of a hollow shaft.
  • the first output shaft is arranged in the intermediate shaft and the intermediate shaft in the further intermediate shaft.
  • the intermediate shaft extends completely through the further intermediate shaft in the axial direction.
  • the first output shaft preferably extends completely through the intermediate shaft in the axial direction.
  • the intermediate shaft, the further intermediate shaft and the first output shaft are arranged coaxially with one another. The described configuration of the intermediate shafts enables a simple and flexible connection of the electrical machine's rule to the torque displacement gear.
  • a preferred further embodiment of the invention provides that the clutch assembly has a connecting shaft that is rigidly coupled to the electrical machine, in particular via a gear stage.
  • the connecting shaft represents a drive shaft of the clutch arrangement.
  • the connecting shaft is rigidly coupled to the electrical machine and to the intermediate shaft and / or the further intermediate shaft (each) connectable.
  • the connecting shaft In the first shift setting of the Heidelbergkupplungsan order, for example, the connecting shaft is coupled to the intermediate shaft, in particular rigidly.
  • the connecting shaft is decoupled from both the intermediate shaft and the further intermediate shaft, so that the electric machine is not drive-connected to the torque displacement gear.
  • the connecting shaft is coupled to the other intermediate shaft, preferably rigidly in turn.
  • the "torque vectoring" functionality can be implemented with the help of the electric machine, whereas in the third shift setting the electric machine is coupled directly to the input shaft and the first output shaft of the transmission device, preferably rigidly.
  • the connection of the connection shaft to the electrical machine is preferably carried out via the gear stage, by means of which a translation between the electrical machine and the connection shaft, in particular different from one, is implemented.
  • the described configuration of the transmission device enables particularly flexible operation.
  • a further embodiment of the invention provides that the intermediate shaft can be coupled by means of a first shift clutch of the shift clutch arrangement and the further intermediate shaft can be coupled to the connecting shaft by means of a second shift clutch of the shift clutch arrangement.
  • the Heidelbergkupp treatment arrangement has the first clutch and the second clutch.
  • the first clutch is arranged in terms of drive technology between the connecting shaft and the intermediate shaft and the second shift clutch in terms of drive technology between the connecting shaft and the further inter-shaft.
  • the intermediate shaft and the further intermediate shaft can be coupled to the connecting shaft independently of one another, namely with the aid of the respective clutch.
  • the first clutch and the second clutch are each designed as one of the following clutches: Non-positive clutch, in particular a special multi-disc clutch, and positive clutch, for example a dog clutch or tooth clutch.
  • the first Heidelbergkupp development is designed as a form-fitting coupling and the second coupling as a force-fitting coupling or vice versa.
  • both clutches can be present as non-positive clutches or as form-fitting clutches.
  • the design of the first clutch as a form-fit clutch and the second clutch as a force-fit clutch enables, on the one hand, an energy-efficient connection of the electrical machine to the input shaft and the second output shaft as well as flexible adjustment of the “torque vectoring” functionality.
  • the reinforcement planetary gear has a reinforcement gearbox sun gear, a reinforcement gearbox hollow wheel and a reinforcement gearbox planetary carrier, the reinforcement gearbox sun gear rigidly coupled to the first sun gear, the reinforcement gearbox ring gear rigidly coupled to the planetary carrier and the reinforcement gearbox planetary carrier rigidly coupled to the second output planetary carrier .
  • On the reinforcement gear planet carrier at least one reinforcement gear planetary gear is rotatably mounted.
  • the reinforcement planetary gear meshes on the one hand with the reinforcement gear sun gear and on the other hand with the reinforcement gear ring gear.
  • the described embodiment of the reinforcing planetary gear enables a particularly high efficiency of the transmission device.
  • the electrical machine viewed in longitudinal section with respect to an axis of rotation of the input shaft, is arranged in overlap with the input shaft.
  • the electrical machine is arranged next to the input shaft when viewed in longitudinal section.
  • the electrical machine is preferably axially parallel to the input shaft.
  • the electrical machine is preferably completely overlapped by the input shaft in the axial direction, so that the input shaft on both sides over the electrical machine protrudes.
  • the electrical machine, seen in longitudinal section is arranged between the planetary carrier of the torque displacement transmission and a gear stage via which the input shaft is drive-coupled to the drive device.
  • the clutch arrangement via which the electrical machine can be coupled to the torque displacement gear, can be arranged on the side of the torque displacement gear facing away from the electrical machine in longitudinal section or in the axial direction.
  • the clutch assembly is arranged on the side of the torque displacement gear facing the electrical machine's rule. Both arrangements have different advantages.
  • the described arrangement of the electric machine enables a particularly compact design of the transmission device.
  • FIG. 1 a schematic representation of a transmission device for a
  • Figure 2 is a schematic representation of the transmission device in the first embodiment, supplemented by a reinforcement tarpaulin gear,
  • FIG. 1 shows a schematic longitudinal sectional illustration of a transmission device 1 for a motor vehicle 2, which is only indicated here in an extremely schematic manner.
  • the transmission device 1 has an input shaft 3, a first output shaft 4 and a second output shaft 5.
  • the input shaft 3 is drive-connected to a drive device 6 of the motor vehicle 2, preferably via a gear change gear 7 and / via a gear stage 8.
  • the gear stage 8 is preferably designed in such a way that a transmission output shaft 9 of the gear change transmission 7 is arranged offset, in particular offset in parallel, to the input shaft 3.
  • the first output shaft 4 and the second output shaft 5 of the gear unit 1 are in the exemplary embodiment shown here with different wheel axles 10 of the motor vehicle 2 in terms of drive technology, whereby only one of the wheel axles 10 is shown here, namely a front wheel axle for example.
  • the first output shaft 4 is connected in terms of drive technology to the wheel axles 10, not shown, which is present, for example, as a rear wheel axle.
  • the second output shaft 5, is drivingly connected to the wheel axles 10 shown, for example via at least one gear stage 1 1, in the exemplary embodiment presented here via several gear stages 1 1 and / or an axle differential gear 12.
  • the transmission device 1 has a torque displacement transmission 13 designed as a planetary transmission.
  • This has a planet carrier 14 on which at least one first planet gear 15 and at least one second planet gear 16 are rotatably mounted.
  • the planet gears 15 and 16 are arranged coaxially to one another and rigidly connected to one another.
  • the torque shift gear 13 is designed as a stepped planetary gear.
  • the first planet gear 15 meshes with a first sun gear 17, the second planet gear 16 with a second sun gear 18.
  • the first sun gear 17 is coupled in terms of drive technology to the second output shaft 5.
  • the second sun In contrast, the internal gear 18 is connected to an electrical machine 20 in terms of drive technology via a clutch assembly 19.
  • the second sun gear 18 is rigidly connected to the clutch arrangement 19 via an intermediate shaft 21 and the planetary carrier 14 via a further intermediate shaft 22.
  • the clutch assembly 19 also has a connecting shaft 23 that is rigidly coupled to the electrical machine 20 in terms of drive technology, preferably via a gear stage 24.
  • the gear stage 24 is designed such that the electrical machine 20 is arranged next to the input shaft 3, in particular in parallel to this is available.
  • the electrical machine 20 is also seen in longitudinal section in overlap with the input shaft 3. In particular, it is seen in the axial direction with respect to an axis of rotation of the input shaft 3 between tween the planet carrier 14 and the gear stage 8. In this way, a space-saving design of the transmission device 1 is achieved.
  • the intermediate shaft 21 is configured as a hollow shaft and receives the first output shaft 4.
  • the other inter mediate shaft 22 is designed as a hollow shaft. It in turn takes the intermediate shaft 21 in itself.
  • the clutch assembly 19 has a first clutch 25 and a second clutch 26.
  • the first clutch 25 is in the form of a non-positive clutch and the second clutch 26 in the form of a positive clutch.
  • the connecting shaft 23 with the inter mediate shaft 21 and with the aid of the clutch 26 with the further inter mediate shaft 22 can be coupled. Accordingly, the electrical machine 20 can be drive-coupled both to the planet carrier 14 and consequently to the input shaft 3 and to the first output shaft 4 and to the second planet gear 16.
  • FIG. 2 shows the first embodiment of the transmission device 1 in schematic form, supplemented by a reinforcement planetary gear 27.
  • This has a reinforcement gear sun gear 28, a reinforcement gear ring gear 29 and a reinforcement gear planet carrier 30.
  • At least one reinforcement gearbox planetary carrier 30 is rotatably mounted on the reinforcement gearbox planetary gear 31, which meshes with both the reinforcement gearbox sun gear 28 and the reinforcement gearbox ring gear 29.
  • the reinforcement gear sun gear 28 is rigidly coupled to the first sun gear 17, the reinforcement gear ring gear 29 rigidly with the planet carrier 14 and the reinforcement gear planet carrier 30 rigidly with the second output shaft 5.
  • FIG. 3 shows a schematic representation of the transmission device 1 in a second embodiment. This corresponds largely to the first embodiment, so that reference is made to the corresponding statements and only the differences are discussed below. These lie in the fact that the clutch assembly 19 is no longer arranged on the side of the torque displacement gear 13 facing away from the electrical machine 20, but rather on the side facing the electrical machine 20. In addition, the intermediate shaft 21 no longer takes the first output shaft 4, but the input shaft 3 and accordingly the second output shaft 5. This also applies to the connecting shaft 23. The further intermediate shaft 22 is formed by the input shaft 3.
  • FIG. 4 shows a schematic representation of the transmission device 1 in the second embodiment, again supplemented by the reinforcement gear 27. To avoid repetition, reference is made to the above statements.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

The invention relates to a transmission device (1) for a motor vehicle (2), which transmission device (1) has an input shaft (3), which is operatively connectable to a drive device (6) of the motor vehicle (2), and a first output shaft (4) and a second output shaft (5), and which transmission device (1) has a torque transfer transmission (13) which is configured as a planetary transmission and via which the input shaft (3) is coupled to the first output shaft (4) and the second output shaft (5). It is provided here that the planetary transmission is a multi-step planetary transmission which has a planetary carrier (14), on which at least one first planetary gear (15) and a second planetary gear (16) which is arranged coaxially with respect to the at least one first planetary gear (15) and is connected fixedly to the latter so as to rotate therewith are mounted rotatably, wherein the first planetary gear (15) meshes with a first sun gear (17) and the second planetary gear (16) meshes with a second sun gear (18), wherein the planetary carrier (14) is coupled fixedly to the input shaft (3) and to the first output shaft (4) so as to rotate therewith, and the first sun gear (17) is coupled fixedly to the second output shaft (5) so as to rotate therewith and/or via a boosting planetary transmission (27), wherein the second sun gear (18) is drive-connected via a shifting clutch arrangement (19) to an electric machine (20).

Description

Getriebeeinrichtung für ein Kraftfahrzeug Transmission device for a motor vehicle
BESCHREIBUNG: Die Erfindung betrifft eine Getriebeeinrichtung für ein Kraftfahrzeug, die eine mit einer Antriebsrichtung des Kraftahrzeugs wirkverbindbare Eingangswelle sowie eine erste Ausgangswelle und eine zweite Ausgangswelle aufweist und über ein als Planetengetriebe ausgestaltetes Drehmomentverlagerungs getriebe verfügt, über das die Eingangswelle mit der ersten Ausgangswelle und der zweiten Ausgangswelle gekoppelt ist. DESCRIPTION: The invention relates to a transmission device for a motor vehicle, which has an input shaft that can be effectively connected to a drive direction of the motor vehicle, as well as a first output shaft and a second output shaft and has a torque displacement gear designed as a planetary gear, via which the input shaft with the first output shaft and the second Output shaft is coupled.
Aus dem Stand der Technik ist beispielsweise die Druckschrift EP 1 494 886 B1 bekannt. Diese betrifft ein Getriebesystem für ein Fahrzeug, wobei das Getriebesystem umfasst: eine Antriebswelle, die mit einem Differenzialme- chanismus verbunden ist, der zwei Abtriebswellen aufweist, wobei die beiden Abtriebswellen jeweils erste und zweite koaxial angebrachte Sonnenräder eines Planetengetriebes tragen, die jeweils in erste und zweite Planeten radsätze eingreifen, wobei das Übersetzungsverhältnis des ersten Sonnen- rads mit dem ersten Planetenradsatz sich von dem des zweiten Sonnenrads mit dem zweiten Planetenradsatz unterscheidet, wobei jedes erste Planeten rad mit einem zugehörigen zweiten Planetenrad verbunden ist, sodass es sich damit um eine zugehörige gemeinsame Planetenwelle dreht, wobei die Planetenwelle mit einem gemeinsamen Träger verbunden ist, der koaxial zum ersten und zweiten Sonnenrad drehbar angebracht ist, ein einzelnes selektiv betätigtes Drehzahlwechselmittel, das mit dem Träger verbunden ist und dazu ausgebildet ist, die Rotationsgeschwindigkeit des Trägers um seine Achse zu erhöhen oder zu verringern, wobei das Getriebesystem weiter min destens einen Sensor umfasst, der dazu ausgebildet ist, ein Signal zu erzeu gen, das einen Betriebsparameter des Fahrzeugs oder seines Motors angibt, und eine Steuereinheit, die mit dem Sensor und dem Drehzahlwechselmittel verbunden und dazu ausgebildet ist, das Drehzahlwechselmittel in Abhän gigkeit von dem Signal zu betätigen. Dabei ist vorgesehen, dass das Dreh zahlwechselmittel ein Elektromotor/-generator ist, dessen Rotor durch selek tiv betätigbare Kopplungsmittel mit dem gemeinsamen Träger und durch zweite selektiv betätigte Kopplungsmittel mit der Antriebswelle oder den bei den Abtriebswellen verbunden ist. The document EP 1 494 886 B1, for example, is known from the prior art. This relates to a transmission system for a vehicle, the transmission system comprising: a drive shaft which is connected to a differential mechanism which has two output shafts, the two output shafts each carrying first and second coaxially mounted sun gears of a planetary gear, each in first and Engage second planetary gear sets, the gear ratio of the first sun gear with the first planetary gear set differs from that of the second sun gear with the second planetary gear set, each first planet gear being connected to an associated second planet gear so that it is an associated common one Planet shaft rotates, the planet shaft being connected to a common carrier which is rotatably mounted coaxially with the first and second sun gears, a single selectively actuated speed change means which is connected to the carrier and is adapted to the rotational speed of the carrier rs to increase or decrease its axis, wherein the transmission system further comprises at least one sensor which is designed to generate a signal that indicates an operating parameter of the vehicle or its engine, and a control unit which is connected to the sensor and the speed change means and is designed to actuate the speed change means in dependence on the signal. It is provided that the speed change means is an electric motor / generator, the rotor of which is connected to the common carrier by selectively operable coupling means and to the drive shaft or to the output shafts by means of second selectively actuated coupling means.
Es ist Aufgabe der Erfindung, eine Getriebeeinrichtung für ein Kraftfahrzeug vorzuschlagen, welche gegenüber bekannten Getriebeeinrichtungen Vorteile aufweist, insbesondere trotz äußerst kompakter Bauform eine„Torque Vec- toring“-Funktionalität zwischen den beiden Ausgangswellen realisiert. The object of the invention is to propose a transmission device for a motor vehicle which has advantages over known transmission devices, in particular realizing a “torque vectoring” functionality between the two output shafts despite an extremely compact design.
Dies wird erfindungsgemäß mit einer Getriebeeinrichtung für ein Kraftfahr zeug mit den Merkmalen des Anspruchs 1 erreicht. Dabei ist vorgesehen, dass das Planetengetriebe ein Stufenplanetengetriebe ist, das einen Plane tenträger aufweist, an dem wenigstens ein erstes Planetenrad sowie ein ko axial zu dem wenigstens einen ersten Planetenrad angeordnetes und dreh fest mit diesem verbundenes zweites Planetenrad drehbar gelagert ist, wobei das erste Planetenrad mit einem ersten Sonnenrad und das zweite Planeten rad mit einem zweiten Sonnenrad kämmt, wobei der Planetenträger mit der Eingangswelle und der ersten Ausgangswelle drehfest gekoppelt und das erste Sonnenrad mit der zweiten Ausgangswelle drehfest und/oder über ein Verstärkungsplanetengetriebe gekoppelt ist, und wobei das zweite Sonnen rad über eine Schaltkupplungsanordnung antriebstechnisch an eine elektri sche Maschine angeschlossen ist. This is achieved according to the invention with a transmission device for a motor vehicle with the features of claim 1. It is provided that the planetary gear is a stepped planetary gear, which has a plane carrier on which at least a first planetary gear and a second planetary gear, which is arranged axially to the at least one first planetary gear and connected to it, are rotatably mounted, the first planetary gear being rotatably mounted with a first sun gear and the second planet gear meshes with a second sun gear, wherein the planet carrier is rotatably coupled to the input shaft and the first output shaft and the first sun gear is rotatably coupled to the second output shaft and / or via a reinforcing planetary gear, and wherein the second sun wheel is connected to an electrical machine via a clutch assembly.
Die Getriebeeinrichtung dient dem Übertragen eines Drehmoments bezie hungsweise Antriebsdrehmoments zwischen der Antriebseinrichtung des Kraftahrzeugs einerseits sowie wenigstens einer Radachse des Kraftfahr zeugs andererseits. Über die Getriebeeinrichtung ist insoweit die wenigstens eine Radachse mit der Antriebsrichtung wirkverbunden beziehungsweise zumindest wirkverbindbar. Die wenigstens eine Radachse liegt entsprechend als angetriebene Radachse vor. Sie kann insbesondere als Vorderradachse oder als Hinterradachse des Kraftahrzeugs ausgestaltet sein. The transmission device is used to transmit a torque or drive torque between the drive device of the motor vehicle on the one hand and at least one wheel axle of the motor vehicle on the other hand. To this extent, the at least one wheel axle is operatively connected or at least operatively connected to the drive direction via the transmission device. The at least one wheel axle is accordingly as a driven wheel axle. It can in particular be designed as a front wheel axle or a rear wheel axle of the motor vehicle.
Beispielsweise ist über die Getriebeeinrichtung lediglich eine einzige Rad achse des Kraftfahrzeugs antreibbar. In diesem Fall dient die Getriebeein richtung insbesondere dem Aufteilen des von der Antriebsrichtung bereitge stellten Antriebsdrehmoments auf unterschiedliche Teilachsen dieser Rad achse, wobei über jede der Teilachsen wenigstens ein Rad des Kraftfahr zeugs antriebstechnisch mit der Getriebeeinrichtung und entsprechend der Antriebseinrichtung gekoppelt oder zumindest koppelbar ist. Die Getriebeein richtung dient insoweit als Achsdifferentialgetriebe. Alternativ kann es vorge sehen sein, dass über die Getriebeeinrichtung mehrere Radachsen antriebs technisch an die Antriebseinrichtung angeschlossen sind. In diesem Fall dient die Getriebeeinrichtung als Mittendifferentialgetriebe der Aufteilung des Antriebsdrehmoments auf die unterschiedlichen Radachsen. Die Radachsen liegen beispielsweise als Vorderradachse sowie als Hinterradachse vor. For example, only a single wheel axis of the motor vehicle can be driven via the transmission device. In this case, the gear unit is used in particular to distribute the drive torque provided by the drive unit to different sub-axles of this wheel axis, with at least one wheel of the motor vehicle being coupled or at least connectable to the gear unit and corresponding to the drive unit via each of the sub-axles. The gear unit serves as an axle differential gear. Alternatively, it can be provided that several wheel axles are technically connected to the drive device via the transmission device. In this case, the gear mechanism serves as a center differential gear to distribute the drive torque to the different wheel axles. The wheel axles are available, for example, as a front wheel axle and a rear wheel axle.
Die Getriebeeinrichtung weist die Eingangswelle sowie die erste Ausgangs welle und die zweite Ausgangswelle auf. Die Eingangswelle der Getriebeein richtung ist an die Antriebseinrichtung des Kraftfahrzeugs antriebstechnisch angeschlossen, vorzugsweise über ein Schaltgetriebe und/oder eine Kupp lung, insbesondere eine Anfahrkupplung. Mittels des Schaltgetriebes kann eine aus mehreren Übersetzungen ausgewählte Übersetzung zwischen der Antriebseinrichtung und der Eingangswelle der Getriebeeinrichtung einge stellt werden. Die Kupplung ist bevorzugt als Schaltkupplung und besonders bevorzugt als Anfahrkupplung ausgestaltet. Mithilfe der Kupplung kann inso weit die Wirkverbindung zwischen der Antriebseinrichtung der Eingangswelle der Getriebeeinrichtung wahlweise hergestellt oder unterbrochen werden. The transmission device has the input shaft and the first output shaft and the second output shaft. The input shaft of the gearbox device is connected in terms of drive technology to the drive device of the motor vehicle, preferably via a gearbox and / or a clutch, in particular a starting clutch. By means of the gearbox, a translation selected from several translations between the drive device and the input shaft of the transmission device can be set. The clutch is preferably designed as a shift clutch and particularly preferably as a starting clutch. With the aid of the clutch, the operative connection between the drive device and the input shaft of the transmission device can be optionally established or interrupted.
Es kann vorgesehen sein, dass die erste Ausgangswelle mit einer ersten Teilwelle der Radachse, insbesondere über ein erstes Getriebe, und die zweite Ausgangswelle mit einer zweiten Teilwelle der Radachse, insbeson dere über ein zweites Getriebe, wirkverbindbar oder wirkverbunden ist. Be sonders bevorzugt ist die erste Ausgangswelle permanent und/oder starr mit der ersten Teilwelle und die zweite Ausgangswelle permanent und/oder starr mit der zweiten Teilwelle gekoppelt. Alternativ kann vorgesehen sein, dass die erste Ausgangswelle mit einer ersten Radachse, insbesondere über das erste Getriebe, und die zweite Ausgangswelle mit der zweiten Radachse, insbesondere über das zweite Getriebe, wirkverbindbar oder wirkverbunden ist. Wiederum ist bevorzugt die erste Ausgangswelle permanent und/oder starr mit der ersten Radachse und die zweite Ausgangswelle permanent und/oder starr mit der zweiten Radachse gekoppelt. Das erste Getriebe und das zweite Getriebe können jeweils als Tellerradgetriebe ausgestaltet sein, sodass die Drehachsen der beiden Teilwellen beziehungsweise der beiden Radachsen jeweils gegenüber den Drehachsen der Ausgangswellen ange winkelt sind, also einen Winkel mit ihnen einschließen, der größer als 0° und kleiner als 180° ist. It can be provided that the first output shaft is operatively connectable or operatively connected to a first partial shaft of the wheel axle, in particular via a first gear, and the second output shaft is operatively connected to a second partial shaft of the wheel axle, in particular via a second gear. The first output shaft is particularly preferably permanent and / or rigid the first partial shaft and the second output shaft permanently and / or rigidly coupled to the second partial shaft. Alternatively, it can be provided that the first output shaft is operatively connectable or operatively connected to a first wheel axle, in particular via the first gear, and the second output shaft is operatively connected to the second wheel axle, in particular via the second gear. Again, the first output shaft is preferably permanently and / or rigidly coupled to the first wheel axle and the second output shaft is permanently and / or rigidly coupled to the second wheel axle. The first gear and the second gear can each be designed as a ring gear, so that the axes of rotation of the two partial shafts or the two wheel axles are angled with respect to the axes of rotation of the output shafts, i.e. they enclose an angle that is greater than 0 ° and less than 180 ° is.
Die Antriebsrichtung verfügt über zumindest ein Antriebsaggregat, welches beispielsweise als Brennkraftmaschine oder als elektrische Maschine ausge staltet ist. Selbstverständlich kann die Antriebsrichtung auch als Hybridan triebseinrichtung vorliegen und insoweit mehrere Antriebsaggregate aufwei sen, welche bevorzugt unterschiedlichen Typs sind. In diesem Fall liegt eines der Antriebsaggregate beispielsweise als Brennkraftmaschine und ein ande res der Antriebsaggregate als elektrische Maschine vor. Verfügt die An triebseinrichtung über mehrere Antriebsaggregate, so ist sie bevorzugt derart ausgestaltet, dass die Antriebsaggregate zumindest zeitweise das auf das Antreiben des Kraftfahrzeugs gerichtete Antriebsdrehmoment gemeinsam bereitstellen. The drive direction has at least one drive unit which is designed, for example, as an internal combustion engine or as an electric machine. Of course, the drive direction can also be present as a hybrid drive device and in this respect have several drive units, which are preferably of different types. In this case, one of the drive units is, for example, an internal combustion engine and another of the drive units is an electrical machine. If the drive device has several drive units, it is preferably designed in such a way that the drive units jointly provide the drive torque aimed at driving the motor vehicle, at least temporarily.
Die Eingangswelle der Getriebeeinrichtung ist über das Drehmomentverlage rungsgetriebe, welches als Planetengetriebe vorliegt, sowohl mit der ersten Ausgangswelle als auch mit der zweiten Ausgangswelle antriebstechnisch gekoppelt, insbesondere permanent. Die Kopplung der Wellen über das Drehmomentverlagerungsgetriebe ist insbesondere drehmomentaufteilend, sodass das an der Eingangswelle bereitgestellte Antriebsdrehmoment auf die erste Ausgangswelle und die zweite Ausgangswelle aufgeteilt wird. Das Drehmomentverlagerungsgetriebe ist ein Differentialgetriebe, welches meh- rere miteinander kämmende Stirnräder aufweist. Ganz allgemein arbeitet das Drehmomentverlagerungsgetriebe als Differentialgetriebe beziehungsweise Ausgleichsgetriebe. The input shaft of the transmission device is drive-coupled via the torque displacement gear, which is present as a planetary gear, both to the first output shaft and to the second output shaft, in particular permanently. The coupling of the shafts via the torque displacement gear is in particular torque-dividing, so that the drive torque provided on the input shaft is divided between the first output shaft and the second output shaft. The torque shift gear is a differential gear, which has several rere having intermeshing spur gears. In general, the torque shift gear works as a differential gear or differential gear.
Das Drehmomentverlagerungsgetriebe weist zwei Sonnenräder, nämlich das erste Sonnenrad und das zweite Sonnenrad, auf. Eines der Sonnenräder ist mit einer der Ausgangswellen gekoppelt, nämlich vorzugsweise starr und/oder permanent. Beispielsweise ist das erste Sonnenrad mit der zweiten Ausgangswelle gekoppelt. Bevorzugt ist jede der Ausgangswelle von der jeweils anderen der Ausgangswellen entkoppelt, also im Rahmen der Getrie beeinrichtung lediglich über das Drehmomentverlagerungsgetriebe mit ihr antriebstechnisch verbunden, insbesondere jedoch nicht drehfest. Insoweit ist zum Beispiel das mit der zweiten Ausgangswelle drehfest gekoppelte ers te Sonnenrad von der ersten Ausgangswelle entkoppelt. Allenfalls sind die Ausgangswellen abseits der Getriebeeinrichtung über die Radachsen und einen Untergrund des Kraftfahrzeugs miteinander verbunden. The torque shift transmission has two sun gears, namely the first sun gear and the second sun gear. One of the sun gears is coupled to one of the output shafts, namely preferably rigidly and / or permanently. For example, the first sun gear is coupled to the second output shaft. Preferably, each of the output shafts is decoupled from the other of the output shafts, that is to say, within the scope of the transmission device, it is only connected to it in terms of drive technology via the torque displacement transmission, but in particular not rotationally fixed. In this respect, for example, the first sun gear, which is coupled in a rotationally fixed manner to the second output shaft, is decoupled from the first output shaft. At most, the output shafts are connected to one another away from the transmission device via the wheel axles and a base of the motor vehicle.
Weiterhin verfügt das Drehmomentverlagerungsgetriebe über den Planeten träger, an welchem das wenigstens eine erste Planetenrad sowie das we nigste eine zweite Planetenrad drehbar gelagert sind. Die Getriebeeinrich tung kann genau ein erstes Planetenrad oder mehrere erste Planetenräder aufweisen. Analog hierzu kann die Getriebeeinrichtung über genau ein zwei tes Planetenrad oder mehrere zweite Planetenräder verfügen. Besonders bevorzugt weist das Drehmomentverlagerungsgetriebe ebenso viele erste Planetenräder wie zweite Planetenräder und umgekehrt auf. Falls im Rah men dieser Beschreibung von dem ersten Planetenrad beziehungsweise dem zweiten Planetenrad die Rede ist, so sind die Ausführungen stets auf das wenigstens eine erste Planetenrad beziehungsweise das wenigste eine zweite Planetenrad bezogen, sofern nicht auf das Gegenteil hingewiesen wird. Furthermore, the torque shift transmission has the planet carrier on which the at least one first planetary gear and the least one second planetary gear are rotatably mounted. The gear device can have exactly one first planetary gear or several first planetary gears. Analogously to this, the transmission device can have exactly one second planetary gear or several second planetary gears. Particularly preferably, the torque shifting gear has as many first planetary gears as there are second planetary gears and vice versa. If the first planetary gear or the second planetary gear is mentioned in the context of this description, the explanations always refer to the at least one first planetary gear or the at least one second planetary gear, unless the contrary is indicated.
Die beiden Planetenräder, also das wenigstens eine erste Planetenrad sowie das wenigste eine zweite Planetenrad, sind koaxial zueinander angeordnet und drehfest miteinander verbunden. Das bedeutet, dass die Planetenräder gemeinsam an dem Planetenträger gelagert sind, insbesondere über eine gemeinsame Welle. Sie weisen bezüglich einer gemeinsamen Drehachse stets dieselbe Drehzahl auf. Hierzu sind sie starr und permanent miteinander verbunden. Das Planetengetriebe kann insoweit auch als Stufenplanetenge triebe bezeichnet werden. Das erste Planetenrad und das zweite Planeten rad können denselben Durchmesser aufweisen. Bevorzugt sind sie jedoch mit unterschiedlichen Durchmessern ausgestaltet. The two planet gears, that is to say the at least one first planet gear and the least one second planet gear, are arranged coaxially to one another and connected to one another in a rotationally fixed manner. That means the planet gears are jointly mounted on the planet carrier, in particular via a common shaft. They always have the same speed with respect to a common axis of rotation. For this they are rigidly and permanently connected to one another. The planetary gear can also be referred to as a stepped planetary gear. The first planetary gear and the second planetary gear can have the same diameter. However, they are preferably designed with different diameters.
Es ist vorgesehen, dass das erste Planetenrad mit dem ersten Sonnenrad und das zweite Planetenrad mit dem zweiten Sonnenrad kämmt. Insbeson dere kämmt das erste Planetenrad ausschließlich mit dem ersten Sonnenrad und das zweite Planetenrad ausschließlich dem zweiten Sonnenrad. Das Drehmomentverlagerungsgetriebe ist insoweit hohlradlos ausgestaltet. Es liegt also kein Hohlrad vor, welches mit dem ersten Planetenrad bezie hungsweise dem zweiten Planetenrad kämmt. Der Planetenträger ist mit der Eingangswelle sowie der ersten Ausgangswelle drehfest gekoppelt. Das be deutet, dass im Rahmen der Getriebeeinrichtung die Eingangswelle starr und permanent mit der ersten Ausgangswelle gekoppelt ist, nämlich über den Planetenträger des Drehmomentverlagerungsgetriebes. Die zweite Aus gangswelle ist hingegen lediglich über das erste Sonnenrad an den Plane tenträger angebunden. Hierzu ist das erste Sonnenrad mit der zweiten Aus gangswelle permanent gekoppelt, nämlich drehfest und/oder über das Ver stärkungsplanetengetriebe. Im Falle der drehfesten Kopplung kann selbst verständlich zwischen dem ersten Sonnenrad und der zweiten Ausgangswel le wenigstens eine Getriebestufe vorliegen, sofern diese die drehfeste bezie hungsweise starre Anbindung des ersten Sonnenrads an die zweite Aus gangswelle gewährleistet. Das Planetengetriebe ist als Plusplanetengetriebe ausgestaltet. It is provided that the first planet gear meshes with the first sun gear and the second planet gear meshes with the second sun gear. In particular, the first planet gear meshes exclusively with the first sun gear and the second planet gear exclusively with the second sun gear. In this respect, the torque shift gear is designed without a ring gear. So there is no ring gear that meshes with the first planet gear or the second planet gear. The planet carrier is rotatably coupled to the input shaft and the first output shaft. This means that, within the framework of the transmission device, the input shaft is rigidly and permanently coupled to the first output shaft, namely via the planetary carrier of the torque displacement transmission. The second output shaft, however, is only connected to the plane carrier via the first sun gear. For this purpose, the first sun gear is permanently coupled to the second output shaft, namely non-rotatably and / or via the reinforcement planetary gear. In the case of the non-rotatable coupling, there can of course be at least one gear stage between the first sun gear and the second output shaft, provided that this ensures the non-rotatable or rigid connection of the first sun gear to the second output shaft. The planetary gear is designed as a plus planetary gear.
Das zweite Sonnenrad ist über die Schaltkupplungsanordnung antriebstech nisch an die elektrische Maschine angeschlossen. Hierdurch wird eine be sonders günstige Integration der elektrischen Maschine in die Getriebeein richtung erzielt. Mittels der Schaltkupplungsanordnung ist die elektrische Ma schine wahlweise mit dem zweiten Sonnenrad koppelbar. Bei einer ersten Schalteinstellung der Schaltkupplungsanordnung ist insoweit die elektrische Maschine mit dem zweiten Sonnenrad gekoppelt, vorzugsweise starr bezie hungsweise drehtest. Bei einer zweiten Schalteinstellung der Schaltkupp lungsanordnung ist hingegen die elektrische Maschine von dem zweiten Sonnenrad entkoppelt. Ist die elektrische Maschine mit dem zweiten Sonnen rad antriebstechnisch gekoppelt, so kann mithilfe der elektrischen Maschine eine Drehmomentaufteilung des an der Eingangswelle anliegenden An triebsdrehmoments auf die erste Ausgangswelle und die zweite Ausgangs welle vorgenommen werden. Die elektrische Maschine ermöglicht insoweit ein sogenanntes“Torque Vectoring“. Gleichzeitig ist die Getriebeeinrichtung sehr kompakt ausgestaltet. The second sun gear is connected to the electrical machine in terms of drive technology via the clutch assembly. As a result, a particularly favorable integration of the electric machine in the gearbox device is achieved. By means of the clutch arrangement, the electrical machine can be optionally coupled to the second sun gear. At a first Switching setting of the clutch assembly is to the extent that the electric machine is coupled to the second sun gear, preferably rigidly or rotated. In the case of a second shift setting of the shift clutch arrangement, however, the electric machine is decoupled from the second sun gear. If the electric machine is drive-connected to the second sun wheel, the electric machine can be used to split the drive torque applied to the input shaft to the first output shaft and the second output shaft. The electrical machine enables so-called “torque vectoring”. At the same time, the transmission device is designed to be very compact.
Eine weitere Ausgestaltung der Erfindung sieht vor, dass das erste Planeten rad und das zweite Planetenrad untereinander unterschiedliche Durchmes ser aufweisen. Hierauf wurde bereits hingewiesen. Die Ausgestaltung der beiden Planetenräder mit unterschiedlichen Durchmessern ermöglicht eine hervorragende Aufteilung des an der Eingangswelle anliegenden Antriebs drehmoments auf die erste Ausgangswelle und die zweite Ausgangswelle mithilfe der elektrischen Maschine. Aufgrund der unterschiedlichen Durch messer der Planetenräder ist zum Aufteilen des Antriebsdrehmoments auf die Ausgangswellen ein vergleichsweise kleines Zusatzdrehmoment der elektrischen Maschine notwendig. Die elektrische Maschine kann insoweit eine deutlich geringere Nennleistung aufweisen als die Antriebseinrichtung des Kraftfahrzeugs. Beispielsweise beträgt die Nennleistung der elektrischen Maschine maximal 50 %, maximal 25 %. maximal 20 %, maximal 15 % oder maximal 10 % der Nennleistung der Antriebseinrichtung. A further embodiment of the invention provides that the first planet wheel and the second planet wheel have different diameters from one another. This has already been pointed out. The design of the two planet gears with different diameters enables an excellent distribution of the drive torque applied to the input shaft between the first output shaft and the second output shaft with the aid of the electric machine. Due to the different diameters of the planetary gears, a comparatively small additional torque of the electrical machine is necessary to distribute the drive torque to the output shafts. To this extent, the electrical machine can have a significantly lower nominal power than the drive device of the motor vehicle. For example, the rated power of the electrical machine is a maximum of 50%, a maximum of 25%. maximum 20%, maximum 15% or maximum 10% of the nominal power of the drive device.
Eine bevorzugte weitere Ausgestaltung der Erfindung sieht vor, dass die Eingangswelle als Hohlwelle ausgestaltet ist und die zweite Ausgangswelle die Eingangswelle zumindest bereichsweise durchgreift. Die zweite Aus gangswelle ist also wenigstens teilweise in der Eingangswelle angeordnet und durchgreift diese. Vorzugsweise erstreckt sich die zweite Ausgangswelle in axialer Richtung bezüglich einer Drehachse der Eingangswelle gesehen vollständig durch die Eingangswelle hindurch. Die Eingangswelle und die zweite Ausgangswelle sind koaxial zueinander angeordnet. Besonders be vorzugt ist auch die erste Ausgangswelle koaxial zu der Eingangswelle und der zweiten Ausgangswelle angeordnet. Die zweite Ausgangswelle ist in und/oder an der Eingangswelle drehbar gelagert. Die Lagerung der zweiten Ausgangswelle an der Eingangswelle wird beispielsweise mithilfe eines in der Eingangswelle angeordneten Lagers realisiert, welches in radialer Rich tung außen an einem Innenumfang der Eingangswelle und in radialer Rich tung innen an einem Außenumfang der zweiten Ausgangswelle angreift. Das Lager ist bevorzugt als Wälzlager ausgestaltet. Es kann jedoch auch als Gleitlager vorliegen. Die beschriebene Ausgestaltung ermöglicht eine kom pakte und platzsparende Ausgestaltung der Getriebeeinrichtung. A preferred further embodiment of the invention provides that the input shaft is designed as a hollow shaft and the second output shaft extends through the input shaft at least in some areas. The second output shaft is at least partially arranged in the input shaft and passes through it. The second output shaft preferably extends completely through the input shaft, viewed in the axial direction with respect to an axis of rotation of the input shaft. The input shaft and the second output shafts are arranged coaxially to one another. The first output shaft is also particularly preferably arranged coaxially with the input shaft and the second output shaft. The second output shaft is rotatably mounted in and / or on the input shaft. The mounting of the second output shaft on the input shaft is realized, for example, with the aid of a bearing arranged in the input shaft, which engages in the radial direction outside on an inner circumference of the input shaft and in the radial direction inside on an outer circumference of the second output shaft. The bearing is preferably designed as a roller bearing. However, it can also be in the form of a plain bearing. The configuration described enables a compact and space-saving configuration of the transmission device.
Im Rahmen einer weiteren Ausführungsform der Erfindung ist vorgesehen, dass das zweite Sonnenrad über eine Zwischenwelle an die Schaltkupp lungsanordnung antriebstechnisch angeschlossen ist. Die Zwischenwelle stellt insoweit die antriebstechnische Verbindung zwischen dem zweiten Sonnenrad und der Schaltkupplungsanordnung her. Vorzugsweise sind das zweite Sonnenrad und die Schaltkupplungsanordnung über die Zwischenwel le starr und/oder permanent miteinander gekoppelt. Beispielsweise erstreckt sich die Zwischenwelle in axialer Richtung aus dem Planetenträger heraus. Die Verwendung der Zwischenwelle ermöglicht auf einfache Art und Weise die Anbindung des Stufenplanetengetriebes an die Schaltkupplungsanord nung. In a further embodiment of the invention it is provided that the second sun gear is connected in terms of drive technology to the clutch arrangement via an intermediate shaft. In this respect, the intermediate shaft establishes the drive connection between the second sun gear and the clutch arrangement. The second sun gear and the clutch arrangement are preferably rigidly and / or permanently coupled to one another via the Zwischenwel le. For example, the intermediate shaft extends out of the planet carrier in the axial direction. The use of the intermediate shaft enables the stepped planetary gear to be connected to the clutch arrangement in a simple manner.
Eine Weiterbildung der Erfindung sieht vor, dass der Planetenträger einer seits drehfest mit der Eingangswelle und andererseits mit einer koaxial zu der Eingangswelle angeordneten weiteren Zwischenwelle drehfest verbun den ist. In axialer Richtung gesehen greifen die Eingangswelle und die weite re Zwischenwelle auf gegenüberliegenden Seiten an dem Planetenträger an. Die Eingangswelle und die weitere Zwischenwelle sind koaxial zueinander angeordnet, weisen also dieselbe Drehachse auf. Die weitere Zwischenwelle dient beispielsweise der Lagerung des Planetenträgers und/oder der an triebstechnischen Anbindung des Planetenträgers an die Schaltkupplungs anordnung. In diesem Fall stellen die Zwischenwelle und die weitere Zwi- schenwelle Abtriebswellen der Schaltkupplungsanordnung dar und sind je weils mit der elektrischen Maschine koppelbar. Hierdurch ist eine einfache und flexible Anbindung der elektrischen Maschine an das Drehmomentverla gerungsgetriebe realisiert. A further development of the invention provides that the planet carrier on the one hand is non-rotatably connected to the input shaft and on the other hand to a further intermediate shaft arranged coaxially with the input shaft. Seen in the axial direction, the input shaft and the wide re intermediate shaft attack on opposite sides of the planet carrier. The input shaft and the further intermediate shaft are arranged coaxially to one another, that is to say they have the same axis of rotation. The further intermediate shaft is used, for example, to support the planetary carrier and / or the drive-related connection of the planetary carrier to the clutch arrangement. In this case, the intermediate shaft and the further intermediate Intermediate shaft represent output shafts of the clutch assembly and can be coupled to the electrical machine each Weil. As a result, a simple and flexible connection of the electrical machine to the torque displacement gear is realized.
Eine weitere bevorzugte Ausführungsform der Erfindung sieht vor, dass die Zwischenwelle und/oder die weitere Zwischenwelle als Hohlwelle ausgebildet sind und die erste Ausgangswelle die Zwischenwelle und/oder die weitere Zwischenwelle zumindest bereichsweise durchgreift. Jede der genannten Wellen, also die Zwischenwelle und die weitere Zwischenwelle, kann als Hohlwelle ausgestaltet sein. Die erste Ausgangswelle durchgreift die jeweili ge Welle vorzugsweise in axialer Richtung vollständig. Die erste Ausgangs welle ist bevorzugt in und/oder an der Zwischenwelle beziehungsweise der weiteren Zwischenwelle gelagert. Zur Lagerung der ersten Ausgangswelle an der jeweiligen Welle ist ein Lager, beispielsweise ein Wälzlager oder ein Gleitlager, vorgesehen. Another preferred embodiment of the invention provides that the intermediate shaft and / or the further intermediate shaft are designed as a hollow shaft and the first output shaft extends through the intermediate shaft and / or the further intermediate shaft at least in regions. Each of the shafts mentioned, that is to say the intermediate shaft and the further intermediate shaft, can be designed as a hollow shaft. The first output shaft extends through the respective ge shaft preferably completely in the axial direction. The first output shaft is preferably mounted in and / or on the intermediate shaft or the further intermediate shaft. A bearing, for example a roller bearing or a plain bearing, is provided for mounting the first output shaft on the respective shaft.
Besonders bevorzugt liegen sowohl die Zwischenwelle als auch die weitere Zwischenwelle als Hohlwelle vor. Hierbei ist die erste Ausgangswelle in der Zwischenwelle und die Zwischenwelle in der weiteren Zwischenwelle ange ordnet. Insbesondere durchgreift die Zwischenwelle die weitere Zwischen welle in axialer Richtung vollständig. Ebenso durchgreift vorzugsweise die erste Ausgangswelle die Zwischenwelle in axialer Richtung vollständig. Die Zwischenwelle, die weitere Zwischenwelle und erste Ausgangswelle sind hierbei koaxial zueinander angeordnet. Die beschriebene Ausgestaltung der Zwischenwellen ermöglicht eine einfache und flexible Anbindung der elektri schen Maschine an das Drehmomentverlagerungsgetriebe. Both the intermediate shaft and the further intermediate shaft are particularly preferably in the form of a hollow shaft. Here, the first output shaft is arranged in the intermediate shaft and the intermediate shaft in the further intermediate shaft. In particular, the intermediate shaft extends completely through the further intermediate shaft in the axial direction. Likewise, the first output shaft preferably extends completely through the intermediate shaft in the axial direction. The intermediate shaft, the further intermediate shaft and the first output shaft are arranged coaxially with one another. The described configuration of the intermediate shafts enables a simple and flexible connection of the electrical machine's rule to the torque displacement gear.
Eine bevorzugte weitere Ausgestaltung der Erfindung sieht vor, dass die Schaltkupplungsanordnung eine Verbindungswelle aufweist, die starr mit der elektrischen Maschine gekoppelt ist, insbesondere über eine Getriebestufe. Die Verbindungswelle stellt insoweit eine Antriebswelle der Schaltkupplungs anordnung dar. Die Verbindungswelle ist starr mit der elektrischen Maschine gekoppelt und mit der Zwischenwelle und/oder der weiteren Zwischenwelle (jeweils) koppelbar. Bei der ersten Schalteinstellung der Schaltkupplungsan ordnung ist insoweit beispielsweise die Verbindungswelle mit der Zwischen welle gekoppelt, insbesondere starr. Bei der zweiten Schalteinstellung der Schaltkupplungsanordnung, welche optional ist, ist hingegen die Verbin dungswelle sowohl von der Zwischenwelle als auch von der weiteren Zwi schenwelle entkoppelt, sodass die elektrische Maschine nicht mit dem Drehmomentverlagerungsgetriebe antriebstechnisch verbunden ist. A preferred further embodiment of the invention provides that the clutch assembly has a connecting shaft that is rigidly coupled to the electrical machine, in particular via a gear stage. The connecting shaft represents a drive shaft of the clutch arrangement. The connecting shaft is rigidly coupled to the electrical machine and to the intermediate shaft and / or the further intermediate shaft (each) connectable. In the first shift setting of the Schaltkupplungsan order, for example, the connecting shaft is coupled to the intermediate shaft, in particular rigidly. In the second shift setting of the clutch arrangement, which is optional, however, the connecting shaft is decoupled from both the intermediate shaft and the further intermediate shaft, so that the electric machine is not drive-connected to the torque displacement gear.
In einer dritten Schalteinstellung der Schaltkupplungsanordnung ist die Ver bindungswelle mit der weiteren Zwischenwelle gekoppelt, vorzugweise wie derum starr. In der ersten Schalteinstellung kann mithilfe der elektrischen Maschine insoweit die„Torque Vectoring“-Funktionalität realisiert sein, wo hingegen in der dritten Schalteinstellung die elektrische Maschine unmittel bar mit der Eingangswelle und der ersten Ausgangswelle der Getriebeein richtung gekoppelt ist, vorzugsweise starr. Die Anbindung der Verbindungs welle an die elektrische Maschine erfolgt bevorzugt über die Getriebestufe, mittels welcher eine insbesondere von eins verschiedene Übersetzung zwi schen der elektrischen Maschine und der Verbindungswelle realisiert ist. Die beschriebene Ausgestaltung der Getriebeeinrichtung ermöglicht einen be sonders flexiblen Betrieb. In a third shift setting of the clutch assembly, the connecting shaft is coupled to the other intermediate shaft, preferably rigidly in turn. In the first shift setting, the "torque vectoring" functionality can be implemented with the help of the electric machine, whereas in the third shift setting the electric machine is coupled directly to the input shaft and the first output shaft of the transmission device, preferably rigidly. The connection of the connection shaft to the electrical machine is preferably carried out via the gear stage, by means of which a translation between the electrical machine and the connection shaft, in particular different from one, is implemented. The described configuration of the transmission device enables particularly flexible operation.
Eine weitere Ausführungsform der Erfindung sieht vor, dass mittels einer ers ten Schaltkupplung der Schaltkupplungsanordnung die Zwischenwelle und mittels einer zweiten Schaltkupplung der Schaltkupplungsanordnung die wei tere Zwischenwelle mit der Verbindungswelle koppelbar ist. Die Schaltkupp lungsanordnung verfügt insoweit über die erste Schaltkupplung und die zwei te Schaltkupplung. Die erste Schaltkupplung ist antriebstechnisch zwischen der Verbindungswelle und der Zwischenwelle und die zweite Schaltkupplung antriebstechnisch zwischen der Verbindungswelle und der weiteren Zwi schenwelle angeordnet. Die Zwischenwelle und die weitere Zwischenwelle sind insoweit unabhängig voneinander mit der Verbindungswelle koppelbar, nämlich mithilfe der jeweiligen Schaltkupplung. Die erste Schaltkupplung und die zweite Schaltkupplung sind jeweils als eine der folgenden Kupplungen ausgestaltet: Kraftschlüssige Kupplung, insbe sondere Lamellenkupplung, und formschlüssige Kupplung, beispielsweise Klauenkupplung oder Zahnkupplung. Beispielsweise ist die erste Schaltkupp lung als formschlüssige Kupplung und die zweite Kupplung als kraftschlüssi ge Kupplung oder umgekehrt ausgestaltet. Ebenso können beide Schalt kupplungen als kraftschlüssige Kupplungen oder als formschlüssige Kupp lungen vorliegen. Die Ausgestaltung der ersten Schaltkupplung als form schlüssige Kupplung und der zweiten Schaltkupplung als kraftschlüssige Kupplung ermöglicht zum einen eine energieeffiziente Anbindung der elektri schen Maschine an die Eingangswelle und die zweite Ausgangswelle sowie eine flexible Einsteilbarkeit der„Torque Vectoring“-Funktionalität. A further embodiment of the invention provides that the intermediate shaft can be coupled by means of a first shift clutch of the shift clutch arrangement and the further intermediate shaft can be coupled to the connecting shaft by means of a second shift clutch of the shift clutch arrangement. The Schaltkupp treatment arrangement has the first clutch and the second clutch. The first clutch is arranged in terms of drive technology between the connecting shaft and the intermediate shaft and the second shift clutch in terms of drive technology between the connecting shaft and the further inter-shaft. The intermediate shaft and the further intermediate shaft can be coupled to the connecting shaft independently of one another, namely with the aid of the respective clutch. The first clutch and the second clutch are each designed as one of the following clutches: Non-positive clutch, in particular a special multi-disc clutch, and positive clutch, for example a dog clutch or tooth clutch. For example, the first Schaltkupp development is designed as a form-fitting coupling and the second coupling as a force-fitting coupling or vice versa. Likewise, both clutches can be present as non-positive clutches or as form-fitting clutches. The design of the first clutch as a form-fit clutch and the second clutch as a force-fit clutch enables, on the one hand, an energy-efficient connection of the electrical machine to the input shaft and the second output shaft as well as flexible adjustment of the “torque vectoring” functionality.
Eine Weiterbildung der Erfindung sieht vor, dass das Verstärkungsplaneten getriebe ein Verstärkungsgetriebesonnenrad, ein Verstärkungsgetriebehohl rad und einen Verstärkungsgetriebeplanetenträger aufweist, wobei das Ver stärkungsgetriebesonnenrad starr mit dem ersten Sonnenrad, das Verstär kungsgetriebehohlrad starr mit dem Planetenträger und der Verstärkungsge triebeplanetenträger starr mit der zweiten Ausgangswelle gekoppelt ist. An dem Verstärkungsgetriebeplanetenträger ist wenigstens ein Verstärkungsge triebeplanetenrad drehbar gelagert. Das Verstärkungsgetriebeplanetenrad kämmt einerseits mit dem Verstärkungsgetriebesonnenrad und andererseits mit dem Verstärkungsgetriebehohlrad. Die beschriebene Ausgestaltung des Verstärkungsplanetengetriebes ermöglicht eine besonders hohe Effizienz der Getriebeeinrichtung. A further development of the invention provides that the reinforcement planetary gear has a reinforcement gearbox sun gear, a reinforcement gearbox hollow wheel and a reinforcement gearbox planetary carrier, the reinforcement gearbox sun gear rigidly coupled to the first sun gear, the reinforcement gearbox ring gear rigidly coupled to the planetary carrier and the reinforcement gearbox planetary carrier rigidly coupled to the second output planetary carrier . On the reinforcement gear planet carrier at least one reinforcement gear planetary gear is rotatably mounted. The reinforcement planetary gear meshes on the one hand with the reinforcement gear sun gear and on the other hand with the reinforcement gear ring gear. The described embodiment of the reinforcing planetary gear enables a particularly high efficiency of the transmission device.
Schließlich kann im Rahmen einer weiteren Ausführungsform der Erfindung vorgesehen sein, dass die elektrische Maschine im Längsschnitt bezüglich einer Drehachse der Eingangswelle gesehen in Überdeckung mit der Ein gangswelle angeordnet ist. In anderen Worten ist die elektrische Maschine im Längsschnitt gesehen neben der Eingangswelle angeordnet. Vorzugswei se liegt die elektrische Maschine achsparallel zu der Eingangswelle vor. Be vorzugt wird die elektrische Maschine in axialer Richtung vollständig von der Eingangswelle Übergriffen, sodass also die Eingangswelle beidseitig über die elektrische Maschine hinausragt. Insbesondere ist die elektrische Maschine im Längsschnitt gesehen zwischen dem Planetenträger des Drehmomentver lagerungsgetriebes und einer Getriebestufe angeordnet, über welche die Eingangswelle mit der Antriebseinrichtung antriebstechnisch gekoppelt ist. Finally, within the scope of a further embodiment of the invention, it can be provided that the electrical machine, viewed in longitudinal section with respect to an axis of rotation of the input shaft, is arranged in overlap with the input shaft. In other words, the electrical machine is arranged next to the input shaft when viewed in longitudinal section. The electrical machine is preferably axially parallel to the input shaft. The electrical machine is preferably completely overlapped by the input shaft in the axial direction, so that the input shaft on both sides over the electrical machine protrudes. In particular, the electrical machine, seen in longitudinal section, is arranged between the planetary carrier of the torque displacement transmission and a gear stage via which the input shaft is drive-coupled to the drive device.
Die Schaltkupplungsanordnung, über welche die elektrische Maschine mit dem Drehmomentverlagerungsgetriebe koppelbar ist, kann im Längsschnitt beziehungsweise in axialer Richtung gesehen auf der der elektrischen Ma schine abgewandten Seite des Drehmomentverlagerungsgetriebes angeord- net sein. Alternativ ist die Schaltkupplungsanordnung auf der der elektri schen Maschine zugewandten Seite des Drehmomentverlagerungsgetriebes angeordnet. Beide Anordnungen haben unterschiedliche Vorteile. Die be schriebene Anordnung der elektrischen Maschine ermöglicht eine besonders kompakte Ausgestaltung der Getriebeeinrichtung. The clutch arrangement, via which the electrical machine can be coupled to the torque displacement gear, can be arranged on the side of the torque displacement gear facing away from the electrical machine in longitudinal section or in the axial direction. Alternatively, the clutch assembly is arranged on the side of the torque displacement gear facing the electrical machine's rule. Both arrangements have different advantages. The described arrangement of the electric machine enables a particularly compact design of the transmission device.
Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert, ohne dass eine Beschränkung der Er findung erfolgt. Dabei zeigt: Figur 1 eine schematische Darstellung einer Getriebeeinrichtung für ein The invention is explained in more detail below with reference to the exemplary embodiments shown in the drawing, without the invention being restricted. It shows: FIG. 1 a schematic representation of a transmission device for a
Kraftfahrzeug in einer ersten Ausführungsform, Motor vehicle in a first embodiment,
Figur 2 eine schematische Darstellung der Getriebeeinrichtung in der ersten Ausführungsform, ergänzt um ein Verstärkungsplane tengetriebe, Figure 2 is a schematic representation of the transmission device in the first embodiment, supplemented by a reinforcement tarpaulin gear,
Figur 3 eine schematische Darstellung der Getriebeeinrichtung in einer zweiten Ausführungsform, sowie Figur 4 eine schematische Darstellung der Getriebeeinrichtung in der zweiten Ausführungsform, wiederum ergänzt um das Verstär kungsplanetengetriebe. Die Figur 1 zeigt eine schematische Längsschnittdarstellung einer Getriebe einrichtung 1 für ein Kraftfahrzeug 2, welches hier lediglich äußerst schema tisch angedeutet ist. Die Getriebeeinrichtung 1 verfügt über eine Eingangs welle 3, eine erste Ausgangswelle 4 sowie über eine zweite Ausgangswelle 5. Die Eingangswelle 3 ist an eine Antriebseinrichtung 6 des Kraftfahrzeugs 2 antriebstechnisch angeschlossen, vorzugsweise über ein Gangwechselge triebe 7 und/über eine Getriebestufe 8. Die Getriebestufe 8 ist vorzugsweise derart ausgestaltet, dass eine Getriebeausgangswelle 9 des Gangwechsel getriebes 7 versetzt, insbesondere parallel versetzt, zu der Eingangswelle 3 angeordnet ist. Figure 3 is a schematic representation of the transmission device in a second embodiment, and Figure 4 is a schematic representation of the transmission device in the second embodiment, again supplemented by the reinforcing planetary gear. FIG. 1 shows a schematic longitudinal sectional illustration of a transmission device 1 for a motor vehicle 2, which is only indicated here in an extremely schematic manner. The transmission device 1 has an input shaft 3, a first output shaft 4 and a second output shaft 5. The input shaft 3 is drive-connected to a drive device 6 of the motor vehicle 2, preferably via a gear change gear 7 and / via a gear stage 8. The gear stage 8 is preferably designed in such a way that a transmission output shaft 9 of the gear change transmission 7 is arranged offset, in particular offset in parallel, to the input shaft 3.
Die erste Ausgangswelle 4 und die zweite Ausgangswelle 5 der Getriebeein richtung 1 sind in dem hier dargestellten Ausführungsbeispiel mit unter schiedlichen Radachsen 10 des Kraftahrzeugs 2 antriebstechnisch gekop pelt, wobei hier lediglich eine der Radachsen 10 dargestellt ist, nämlich bei spielsweise eine Vorderradachse. Die erste Ausgangswelle 4 ist an die nicht dargestellte der Radachsen 10 antriebstechnisch angeschlossen, welche beispielsweise als Hinterradachse vorliegt. Die zweite Ausgangswelle 5 ist hingegen mit der dargestellten der Radachsen 10 antriebstechnisch verbun den, beispielsweise über wenigstens eine Getriebestufe 1 1 , in dem hier dar gestellten Ausführungsbeispiel über mehrere Getriebestufen 1 1 , und/oder ein Achsdifferentialgetriebe 12. The first output shaft 4 and the second output shaft 5 of the gear unit 1 are in the exemplary embodiment shown here with different wheel axles 10 of the motor vehicle 2 in terms of drive technology, whereby only one of the wheel axles 10 is shown here, namely a front wheel axle for example. The first output shaft 4 is connected in terms of drive technology to the wheel axles 10, not shown, which is present, for example, as a rear wheel axle. The second output shaft 5, on the other hand, is drivingly connected to the wheel axles 10 shown, for example via at least one gear stage 1 1, in the exemplary embodiment presented here via several gear stages 1 1 and / or an axle differential gear 12.
Die Getriebeeinrichtung 1 verfügt über ein als Planetengetriebe ausgestalte tes Drehmomentverlagerungsgetriebe 13. Dieses weist einen Planetenträger 14 auf, an dem wenigstens ein erstes Planetenrad 15 sowie wenigstens ein zweites Planetenrad 16 drehbar gelagert sind. Die Planetenräder 15 und 16 sind koaxial zueinander angeordnet und starr miteinander verbunden. Das Drehmomentverlagerungsgetriebe 13 ist insoweit als Stufenplanetengetriebe ausgestaltet. Das erste Planetenrad 15 kämmt mit einem ersten Sonnenrad 17, das zweite Planetenrad 16 mit einem zweiten Sonnenrad 18. Das erste Sonnenrad 17 ist in dem hier dargestellten Ausführungsbeispiel drehfest mit der zweiten Ausgangswelle 5 antriebstechnisch gekoppelt. Das zweite Son- nenrad 18 ist hingegen über eine Schaltkupplungsanordnung 19 antriebs technisch an eine elektrische Maschine 20 angeschlossen. The transmission device 1 has a torque displacement transmission 13 designed as a planetary transmission. This has a planet carrier 14 on which at least one first planet gear 15 and at least one second planet gear 16 are rotatably mounted. The planet gears 15 and 16 are arranged coaxially to one another and rigidly connected to one another. The torque shift gear 13 is designed as a stepped planetary gear. The first planet gear 15 meshes with a first sun gear 17, the second planet gear 16 with a second sun gear 18. In the exemplary embodiment shown here, the first sun gear 17 is coupled in terms of drive technology to the second output shaft 5. The second sun In contrast, the internal gear 18 is connected to an electrical machine 20 in terms of drive technology via a clutch assembly 19.
Es ist erkennbar, dass das zweite Sonnenrad 18 über eine Zwischenwelle 21 und der Planetenträger 14 über eine weitere Zwischenwelle 22 starr an die Schaltkupplungsanordnung 19 angeschlossen sind. Die Schaltkupplungsan ordnung 19 verfügt zudem über eine Verbindungswelle 23, die starr mit der elektrischen Maschine 20 antriebstechnisch gekoppelt ist, vorzugsweise über eine Getriebestufe 24. Die Getriebestufe 24 ist hierbei derart ausgestaltet, dass die elektrische Maschine 20 neben der Eingangswelle 3 angeordnet ist, insbesondere parallel zu dieser vorliegt. In dem hier dargestellten Ausfüh rungsbeispiel liegt die elektrische Maschine 20 zudem im Längsschnitt gese hen in Überdeckung mit der Eingangswelle 3 vor. Insbesondere ist sie in axi aler Richtung bezüglich einer Drehachse der Eingangswelle 3 gesehen zwi schen dem Planetenträger 14 und der Getriebestufe 8 angeordnet. Hierdurch wird eine platzsparende Ausgestaltung der Getriebeeinrichtung 1 erzielt. It can be seen that the second sun gear 18 is rigidly connected to the clutch arrangement 19 via an intermediate shaft 21 and the planetary carrier 14 via a further intermediate shaft 22. The clutch assembly 19 also has a connecting shaft 23 that is rigidly coupled to the electrical machine 20 in terms of drive technology, preferably via a gear stage 24. The gear stage 24 is designed such that the electrical machine 20 is arranged next to the input shaft 3, in particular in parallel to this is available. In the exemplary embodiment shown here, the electrical machine 20 is also seen in longitudinal section in overlap with the input shaft 3. In particular, it is seen in the axial direction with respect to an axis of rotation of the input shaft 3 between tween the planet carrier 14 and the gear stage 8. In this way, a space-saving design of the transmission device 1 is achieved.
Es ist weiter erkennbar, dass die Zwischenwelle 21 als Hohlwelle ausgestal tet ist und die erste Ausgangswelle 4 in sich aufnimmt. Auch die weitere Zwi schenwelle 22 ist als Hohlwelle ausgestaltet. Sie nimmt wiederum die Zwi schenwelle 21 in sich auf. Die Schaltkupplungsanordnung 19 verfügt über eine erste Schaltkupplung 25 und eine zweite Schaltkupplung 26. Die erste Schaltkupplung 25 liegt in Form einer kraftschlüssigen Kupplung und die zweite Schaltkupplung 26 in Form einer formschlüssigen Kupplung vor. Mit hilfe der ersten Schaltkupplung 25 ist die Verbindungswelle 23 mit der Zwi schenwelle 21 und mithilfe der Schaltkupplung 26 mit der weiteren Zwi schenwelle 22 koppelbar. Entsprechend kann die elektrische Maschine 20 sowohl mit dem Planetenträger 14 und mithin der Eingangswelle 3 sowie der erste Ausgangswelle 4 als auch mit dem zweiten Planetenrad 16 antriebs technisch gekoppelt werden. Es kann somit mithilfe der elektrischen Maschi ne 20 das von der Antriebseinrichtung 6 bereitgestellte Antriebsdrehmoment unterstützt oder das Antriebsdrehmoment auf die Ausgangswellen 4 und 5 einstellbar verteilt werden, sodass eine„Torque Vectoring“-Funktionalität rea lisiert ist. Die Figur 2 zeigt die erste Ausführung der Getriebeeinrichtung 1 in schemati scher Form, ergänzt um ein Verstärkungsplanetengetriebe 27. Dieses weist ein Verstärkungsgetriebesonnenrad 28, ein Verstärkungsgetriebehohlrad 29 und einen Verstärkungsgetriebeplanetenträger 30 auf. An dem Verstär kungsgetriebeplanetenträger 30 ist wenigstens ein Verstärkungsgetriebepla netenrad 31 drehbar gelagert, das sowohl mit dem Verstärkungsgetriebe sonnenrad 28 als auch dem Verstärkungsgetriebehohlrad 29 kämmt. Das Verstärkungsgetriebesonnenrad 28 ist starr mit dem ersten Sonnenrad 17, dass Verstärkungsgetriebehohlrad 29 starr mit dem Planetenträger 14 und der Verstärkungsgetriebeplanetenträger 30 starr mit der zweiten Ausgangs welle 5 antriebstechnisch gekoppelt. It can also be seen that the intermediate shaft 21 is configured as a hollow shaft and receives the first output shaft 4. The other inter mediate shaft 22 is designed as a hollow shaft. It in turn takes the intermediate shaft 21 in itself. The clutch assembly 19 has a first clutch 25 and a second clutch 26. The first clutch 25 is in the form of a non-positive clutch and the second clutch 26 in the form of a positive clutch. With the help of the first clutch 25, the connecting shaft 23 with the inter mediate shaft 21 and with the aid of the clutch 26 with the further inter mediate shaft 22 can be coupled. Accordingly, the electrical machine 20 can be drive-coupled both to the planet carrier 14 and consequently to the input shaft 3 and to the first output shaft 4 and to the second planet gear 16. With the aid of the electrical machine 20, the drive torque provided by the drive device 6 can thus be supported or the drive torque can be adjustably distributed to the output shafts 4 and 5, so that a “torque vectoring” functionality is implemented. FIG. 2 shows the first embodiment of the transmission device 1 in schematic form, supplemented by a reinforcement planetary gear 27. This has a reinforcement gear sun gear 28, a reinforcement gear ring gear 29 and a reinforcement gear planet carrier 30. At least one reinforcement gearbox planetary carrier 30 is rotatably mounted on the reinforcement gearbox planetary gear 31, which meshes with both the reinforcement gearbox sun gear 28 and the reinforcement gearbox ring gear 29. The reinforcement gear sun gear 28 is rigidly coupled to the first sun gear 17, the reinforcement gear ring gear 29 rigidly with the planet carrier 14 and the reinforcement gear planet carrier 30 rigidly with the second output shaft 5.
Die Figur 3 zeigt eine schematische Darstellung der Getriebeeinrichtung 1 in einer zweiten Ausführungsform. Diese entspricht weitestgehend der ersten Ausführungsform, sodass auf die entsprechenden Ausführungen verwiesen und nachfolgend lediglich auf die Unterschiede eingegangen wird. Diese lie gen darin, dass die Schaltkupplungsanordnung 19 nun nicht mehr auf der der elektrischen Maschine 20 abgewandten Seite des Drehmomentverlage rungsgetriebes 13 angeordnet ist, sondern vielmehr auf der der elektrischen Maschine 20 zugewandten Seite. Zudem nimmt nun die Zwischenwelle 21 nicht mehr die erste Ausgangswelle 4, sondern die Eingangswelle 3 und ent sprechend die zweite Ausgangswelle 5 auf. Dies gilt ebenso für die Verbin dungswelle 23. Die weitere Zwischenwelle 22 ist von der Eingangswelle 3 gebildet. FIG. 3 shows a schematic representation of the transmission device 1 in a second embodiment. This corresponds largely to the first embodiment, so that reference is made to the corresponding statements and only the differences are discussed below. These lie in the fact that the clutch assembly 19 is no longer arranged on the side of the torque displacement gear 13 facing away from the electrical machine 20, but rather on the side facing the electrical machine 20. In addition, the intermediate shaft 21 no longer takes the first output shaft 4, but the input shaft 3 and accordingly the second output shaft 5. This also applies to the connecting shaft 23. The further intermediate shaft 22 is formed by the input shaft 3.
Die Figur 4 zeigt eine schematische Darstellung der Getriebeeinrichtung 1 in der zweiten Ausführungsform, wiederum ergänzt um das Verstärkungsge triebe 27. Um Wiederholungen zu vermeiden, wird auf die vorstehenden Aus führungen verwiesen. FIG. 4 shows a schematic representation of the transmission device 1 in the second embodiment, again supplemented by the reinforcement gear 27. To avoid repetition, reference is made to the above statements.

Claims

PATENTANSPRÜCHE: PATENT CLAIMS:
1. Getriebeeinrichtung (1 ) für ein Kraftfahrzeug (2), die eine mit einer Antriebseinrichtung (6) des Kraftfahrzeugs (2) wirkverbindbare Eingangswel le (3) sowie eine erste Ausgangswelle (4) und eine zweite Ausgangswelle (5) aufweist und über ein als Planetengetriebe ausgestaltetes Drehmomentver lagerungsgetriebe (13) verfügt, über das die Eingangswelle (3) mit der ersten Ausgangswelle (4) und der zweiten Ausgangswelle (5) gekoppelt ist, dadurch gekennzeichnet, dass das Planetengetriebe ein Stufenplanetenge triebe ist, das einen Planetenträger (14) aufweist, an dem mindestens ein erstes Planetenrad (15) sowie ein koaxial zu dem wenigstens einen ersten Planetenrad (15) angeordnetes und drehfest mit diesem verbundenes zwei tes Planetenrad (16) drehbar gelagert sind, wobei das erste Planetenrad (15) mit einem ersten Sonnenrad (17) und das zweite Planetenrad (16) mit einem zweiten Sonnenrad (18) kämmt, wobei der Planetenträger (14) mit der Ein gangswelle (3) und der ersten Ausgangswelle (4) drehfest gekoppelt und das erste Sonnenrad (17) mit der zweiten Ausgangswelle (5) drehfest und/oder über ein Verstärkungsplanetengetriebe (27) gekoppelt ist, wobei das zweite Sonnenrad (18) über eine Schaltkupplungsanordnung (19) antriebstechnisch an eine elektrische Maschine (20) angeschlossen ist. 1. Transmission device (1) for a motor vehicle (2), which has an input shaft (3) operatively connectable to a drive device (6) of the motor vehicle (2) and a first output shaft (4) and a second output shaft (5) and via a A torque displacement gear (13) designed as a planetary gear, via which the input shaft (3) is coupled to the first output shaft (4) and the second output shaft (5), characterized in that the planetary gear is a stepped planetary gear which has a planet carrier (14 ), on which at least one first planet gear (15) and one coaxially to the at least one first planet gear (15) arranged and rotatably connected to this two th planet gear (16) are rotatably mounted, the first planet gear (15) with a first Sun gear (17) and the second planet gear (16) meshes with a second sun gear (18), the planet carrier (14) with the input shaft (3) and the first output shaft (4th ) coupled non-rotatably and the first sun gear (17) is non-rotatably coupled to the second output shaft (5) and / or via a reinforcing planetary gear (27), the second sun gear (18) being connected to an electrical machine (20) via a clutch arrangement (19) ) connected.
2. Getriebeeinrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das erste Planetenrad (15) und das zweite Planetenrad (16) unterei nander unterschiedliche Durchmesser aufweisen. 2. Transmission device according to claim 1, characterized in that the first planet gear (15) and the second planet gear (16) have different diameters below one another.
3. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Eingangswelle (3) als Hohlwelle ausge staltet ist und die zweite Ausgangswelle (5) die Eingangswelle (13) zumin dest bereichsweise durchgreift. 3. Transmission device according to one of the preceding claims, characterized in that the input shaft (3) is designed as a hollow shaft and the second output shaft (5) extends through the input shaft (13) at least in regions.
4. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das zweite Sonnenrad (18) über eine Zwi schenwelle (21 ) an die Schaltkupplungsanordnung (19) antriebstechnisch angeschlossen ist. 4. Transmission device according to one of the preceding claims, characterized in that the second sun gear (18) is connected in terms of drive technology to the clutch assembly (19) via an inter mediate shaft (21).
5. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Planetenträger (14) einerseits drehtest mit der Eingangswelle (3) und andererseits mit einer koaxial zu der Ein gangswelle (3) angeordneten weiteren Zwischenwelle (22) drehtest verbun den ist. 5. Transmission device according to one of the preceding claims, characterized in that the planet carrier (14) on the one hand rotates with the input shaft (3) and on the other hand with a coaxially to the input shaft (3) arranged further intermediate shaft (22) rotates verbun the is.
6. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Zwischenwelle (21 ) und/oder die weitere Zwischenwelle (22) als Hohlwelle ausgebildet sind und die erste Ausgangs welle (4) die Zwischenwelle (21 ) und/oder die weitere Zwischenwelle (22) zumindest bereichsweise durchgreift. 6. Transmission device according to one of the preceding claims, characterized in that the intermediate shaft (21) and / or the further intermediate shaft (22) are designed as a hollow shaft and the first output shaft (4) the intermediate shaft (21) and / or the further intermediate shaft (22) reaches through at least in some areas.
7. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Schaltkupplungsanordnung (19) eine Verbindungswelle (33) aufweist, die starr mit der elektrischen Maschine (20) gekoppelt ist. 7. Transmission device according to one of the preceding claims, characterized in that the clutch assembly (19) has a connecting shaft (33) which is rigidly coupled to the electrical machine (20).
8. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mittels einer ersten Schaltkupplung (25) der Schaltkupplungsanordnung (19) die Zwischenwelle (21 ) und mittels einer zweiten Schaltkupplung (26) der Schaltkupplungsanordnung (19) die weitere Zwischenwelle (21 ) mit der Verbindungswelle (23) koppelbar ist. 8. Transmission device according to one of the preceding claims, characterized in that by means of a first clutch (25) of the clutch arrangement (19) the intermediate shaft (21) and by means of a second clutch (26) of the clutch arrangement (19) with the further intermediate shaft (21) the connecting shaft (23) can be coupled.
9. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Verstärkungsplanetengetriebe (27) ein Verstärkungsgetriebesonnenrad (28), Verstärkungsgetriebehohlrad (29) und einen Verstärkungsgetriebeplanetenträger (30) aufweist, wobei das Verstär kungsgetriebesonnenrad (28) starr mit dem ersten Sonnenrad (17), das Ver stärkungsgetriebehohlrad (29) starr mit dem Planetenträger (14) und der Verstärkungsgetriebeplanetenträger (30) starr mit der zweiten Ausgangswel le (5) gekoppelt ist. 9. Transmission device according to one of the preceding claims, characterized in that the reinforcement planetary gear (27) has a reinforcement gear sun gear (28), reinforcement gear ring gear (29) and a reinforcement gear planet carrier (30), the reinforcement gear sun gear (28) rigidly connected to the first sun gear (17) ), the United strengthening gear ring gear (29) rigidly coupled to the planet carrier (14) and the reinforcing gear planet carrier (30) rigidly coupled to the second output shaft (5).
10. Getriebeeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die elektrische Maschine (20) im Längs schnitt bezüglich einer Drehachse der Eingangswelle (3) gesehen in Überde ckung mit der Eingangswelle (3) angeordnet ist. 10. Transmission device according to one of the preceding claims, characterized in that the electrical machine (20) in longitudinal section with respect to an axis of rotation of the input shaft (3) is arranged in Überde cover with the input shaft (3).
PCT/EP2020/050355 2019-02-08 2020-01-09 Transmission device for a motor vehicle WO2020160865A1 (en)

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