WO2024031122A1 - Drive unit for a motor vehicle - Google Patents

Drive unit for a motor vehicle Download PDF

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Publication number
WO2024031122A1
WO2024031122A1 PCT/AT2023/060272 AT2023060272W WO2024031122A1 WO 2024031122 A1 WO2024031122 A1 WO 2024031122A1 AT 2023060272 W AT2023060272 W AT 2023060272W WO 2024031122 A1 WO2024031122 A1 WO 2024031122A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
drive unit
gears
drive machine
input shaft
Prior art date
Application number
PCT/AT2023/060272
Other languages
German (de)
French (fr)
Inventor
Vitaly Davydov
Gernot Fuckar
Manuel Gruber
Original Assignee
Avl List Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Avl List Gmbh filed Critical Avl List Gmbh
Publication of WO2024031122A1 publication Critical patent/WO2024031122A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • 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
    • B60K6/22—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
    • 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
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • 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
    • B60K2006/381—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 characterized by driveline brakes
    • 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
    • B60K2006/4816—Electric machine connected or connectable to gearbox internal shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W2300/00—Indexing codes relating to the type of vehicle
    • B60W2300/36—Cycles; Motorcycles; Scooters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/10—Road Vehicles
    • B60Y2200/12—Motorcycles, Trikes; Quads; Scooters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/42—Clutches or brakes
    • B60Y2400/421—Dog type clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds

Definitions

  • the invention relates to a drive unit for a motor vehicle, in particular for a motorcycle, with a primary drive machine, a secondary drive machine and a transmission, which drive unit has:
  • a planetary gear set having first, second and third links, the first link being connected to the primary drive machine, the second link being connected to the secondary drive machine and the third link being connected to the first input shaft;
  • At least one first switching element which is designed to connect two members of the planetary gear set to one another in a rotationally fixed manner in a switching position and to connect and block the drive machine with the housing in a further switching position;
  • the idler gears of at least two pairs of gears are rotatably mounted on the intermediate shaft, and the fixed gears of these at least two pairs of gears are arranged in a rotationally fixed manner on the input shaft.
  • the invention further relates to a motor vehicle, in particular a motorcycle, with such a drive unit.
  • WO 00/20243 A1 discloses a drive unit with an internal combustion engine, an electric machine, a transmission with an input shaft and an intermediate shaft and a planetary gear.
  • the transmission has a gear pair arrangement with several pairs of gears, with fixed gears Gear pair arrangements are arranged on the input shaft and idler gears on the intermediate shaft. The idler gears can be switched via switching elements.
  • Transmission arrangement with an internal combustion engine and an electric machine which transmission arrangement has a gear change transmission, a planetary gear and two transmission input shafts, which are connected to one of the electric machine via the planetary gear.
  • the object of the invention is to provide a compact drive unit with a high level of switching comfort.
  • ilPGS> 1 where iiPGs is a transmission ratio of the planetary gear set (PGS) from the first link (PI) to the input shaft (14) with the secondary drive machine (EM) stopped, and that the gear ratios IG2, ics, iG6, IIPGS satisfy at least one of the following inequalities:
  • the transmission has a progressive gear ratio, whereby the following applies to the ratios i G i, iG2, iG3, iG4, ics, ie:
  • the first member of the planetary gear set is designed as a ring gear
  • the second member of the planetary gear set is designed as a sun gear
  • the third member of the planetary gear set is designed as a web.
  • the idler gear of a gear pair is rotatably mounted on the input shaft, and the fixed gear of this gear pair is arranged in a rotationally fixed manner on the first intermediate shaft.
  • the planetary gear set can be arranged between the gear pair arrangement and the secondary drive machine.
  • the secondary drive machine is arranged coaxially with the planetary gear set.
  • the primary drive machine is arranged coaxially with the planetary gear set and the secondary drive machine and at a distance from the input shaft.
  • a further embodiment variant of the invention provides that the idler gear of a pair of gears is rotatably mounted on the first intermediate shaft and the idler gear of another pair of gears is rotatably mounted on a second intermediate shaft, the two idler gears meshing with a common fixed gear on the input shaft.
  • the two pairs of gears therefore share a common fixed gear. This allows components and installation space to be saved.
  • the idler gears of at least three pairs of gears are rotatably mounted on the intermediate shaft, and the fixed gears of these at least three pairs of gears are arranged in a rotationally fixed manner on the input shaft, preferably the idler gear of a reverse gear stage on an intermediate shaft, preferably the first Intermediate shaft, is rotatably mounted.
  • the primary drive machine is arranged coaxially with the planetary gear set and the secondary drive machine is arranged parallel and at a distance from the input shaft.
  • the invention provides that the primary drive machine is arranged coaxially with the secondary drive machine.
  • a parking lock device can be dispensed with.
  • the drive unit has a parking lock device with at least one lockable parking lock wheel, the parking lock wheel being arranged on the first intermediate shaft or the second intermediate shaft.
  • At least one switching element is formed by an axially displaceable switching sleeve, preferably an axially displaceable double switching sleeve. At least one switching element advantageously has two switching positions and preferably a neutral position between a first and a second switching position.
  • the idler gears of gear pairs can be switched, i.e. activated or deactivated, by the second or third switching element.
  • at least one idler gear is activated and the other is deactivated in each of the switching positions.
  • In the neutral position both idler gears of the neighboring gear pairs are deactivated.
  • Activated means that the idler gear is connected to the intermediate shaft in a rotation-proof manner.
  • Deactivated means that the corresponding idler gear is decoupled from the intermediate shaft, i.e. it can rotate freely on it.
  • the first switching element is designed in one piece with a fixed gear of at least one adjacent pair of gears. This allows installation space and the number of parts to be saved.
  • the fixed gear is moved axially with the first switching element during the switching process. This design requires degree gearing of the gears of the affected gear pair.
  • the primary drive machine is advantageously formed by an internal combustion engine and the secondary drive machine by an electrical machine.
  • the object can further be achieved with a motor vehicle, for example a motorcycle, with a drive unit in which, according to the invention, the transmission is designed to carry out at least one gear change - preferably from first to second gear - with active torque replenishment by the secondary drive machine.
  • the comfort of switching operations can be significantly improved.
  • FIG. 1 shows a motor vehicle with a drive unit according to the invention
  • FIG. 2 shows a drive unit according to the invention in a first embodiment variant
  • FIG. 3 shows a drive unit according to the invention in a second embodiment variant
  • FIG. 4 shows a drive unit according to the invention in a third embodiment variant
  • FIG. 5 shows a drive unit according to the invention in a fourth embodiment variant
  • FIG. 6 shows a drive unit according to the invention in a fifth embodiment variant
  • FIG. 7 shows a drive unit according to the invention in a sixth embodiment variant.
  • Fig. 8 shows a gear change map of the drive unit according to the invention.
  • Fig. 1 shows a motorcycle 11 with a drive unit 12 according to the invention, consisting of a primary drive machine ICE, a secondary drive machine EM and a transmission 13 with transversely arranged parallel input 14, intermediate 16 and output shafts 17.
  • the output shaft 17 is via one in the exemplary embodiment shown
  • Final drive formed by a traction mechanism FD for example, is drive-connected to a rear wheel 19 of the motorcycle 1 via a drive chain 18.
  • the primary drive machine ICE is formed by an internal combustion engine and the secondary drive unit EM by an electric machine.
  • Fig. 2 the drive unit 12 from Fig. 1 is shown in detail.
  • the transmission 13 of the drive unit 12 is designed in each of the embodiment variants to carry out at least two gear changes with active torque support by the secondary drive machine EM.
  • the transmission 13 has an input shaft 14.
  • the output shaft 17 is connected in a rotationally fixed manner to a first intermediate shaft 16 or is designed in one piece with it.
  • the first intermediate shaft 16 is arranged parallel to the input shaft 14.
  • the transmission 13 has a planetary gear set PGS with a first PI, second P2 and third link P3, the first link PI being connected to the primary drive machine ICE, the second link P2 to the secondary drive machine EM and the third link P3 to the input shaft 14.
  • the primary drive machine is drive-connected to the first member PI of the planetary gear set PGS via a primary drive PD formed by a spur gear stage.
  • the transmission 13 has a gear pair arrangement 20 with three gear pairs 1/2, 3/5, 4/6, each gear pair 1/2, 3/5, 4/6, a fixed gear 2F, 5F, 6F and an idler gear 2L, 5L , 6L, which correspond to each other and are in tooth mesh.
  • Fixed gears are gears that are connected in a rotationally fixed manner to the respective supporting shaft - for example the input shaft 14 or the first intermediate shaft 16.
  • Idler gears are gears that are rotatably mounted on the supporting shaft - the first intermediate shaft 16 or the input shaft 14.
  • the idler gear 2L, 5L, 6L and the fixed gear 2F, 5F, 6F of each gear pair 1/2, 3/5, 4/6 are therefore arranged on different supporting shafts, the supporting shafts being arranged parallel and spaced apart from one another in the gear 13.
  • the idler gears 2L, 6L of the gear pairs 1/2, 4/6 are rotatably arranged on the first intermediate shaft 16.
  • Two gears of two pairs of gears 1/2, 4/6, each formed by a fixed gear 2F, 6F, are arranged on and non-rotatably with the input shaft 14.
  • the idler gear L5 of the gear pair 3/5 is on the input shaft 14 rotatably arranged.
  • the fixed gear F5 of the gear pair 3/5 is arranged on and non-rotatably with the first intermediate shaft 16.
  • a first switching element CI, a second switching element C2 and a third switching element C3 are provided.
  • Each of the switching elements CI, C2, C3 designed as a switching sleeve has two switching positions.
  • the first CI and third switching element C3 is designed as a double switching sleeve and also has a neutral position N between the two switching positions.
  • the first switching element CI blocks the primary drive machine ICE in the first switching position L - the left switching position in FIG. 2 - by establishing a rotary connection with the housing H.
  • the second switching position R - right in FIG. 2 - the first link PI and the third link P3 of the planetary gear set PGS are coupled to one another in a rotationally fixed manner.
  • the neutral position N the non-rotatable connection with the housing H or between the two members PI and P3 is canceled.
  • the second switching element C2 is used in the first embodiment variant shown in FIG. 2 to activate or deactivate the idler gear L5 of the gear pair 3/5.
  • the switching sleeve of the second switching element C2 is firmly connected to the fixed gear 6F of the gear pair 4/6 or is formed in one piece with it.
  • the idler gear L5 is deactivated, i.e. separated from the input shaft 14.
  • the idler gear L5 is activated, i.e. connected to the input shaft 14 in a rotationally fixed manner.
  • the third switching element C3 is used to activate or deactivate the idler gear L6 of the gear pair 4/6 and the idler gear L2 of the gear pair 1/2.
  • the first - left in FIG. In the second switching position of the second switching element C3 - right in FIG.
  • the Neutral position N of the third switching element C3 In the Neutral position N of the third switching element C3, the rotationally fixed connection between the idler gears L6 and L2 with the first intermediate shaft 16 is interrupted, the idler gears 6L and 2L are freely rotatable on the supporting first intermediate shaft 16.
  • the gears on the input shaft 14 have gear ratios iG2 - for the gear pair 1/2 ics - for the gear pair 3/5 - and ice - for the gear pair 4/6 - with the gears on the first intermediate shaft 16.
  • iiPGs denotes a transmission ratio of the planetary gear set PGS from the second input shaft 15 to the first input shaft 14 when the secondary drive machine EM is stopped. This transmission ratio iiPGs is greater than 1 in all embodiment variants according to the invention:
  • gear ratios IG2, IG3, IGS, iG6, IIPGS fulfill at least one of the following inequalities:
  • the transmission 13 has a progressive gear gradation of the gears Gl, G2, G3, G4, G5, G6, whereby the following applies to the translations i G i, iG2, IG3, iG4, ics, ie: The following applies to the translations SIPGS, IGI, iG2:
  • Fig. 8 shows a gear change map of the drive unit 12 according to the invention.
  • the progressive gear gradation can be clearly seen by the dashed lines. 2 to 7, the first link PI of the planetary gear set PGS is designed as a ring gear, the second link P2 of the planetary gear set PGS is designed as a sun gear and the third link P3 of the planetary gear set PGS is designed as a planet carrier.
  • zi is the number of teeth of the sun gear
  • Z2 is the number of teeth of the ring gear.
  • the transmission 13 has a total of 6 gears Gl, G2, G3, G4, G5, G6 for ICE or hybrid operation.
  • ICE or hybrid operating modes are operating modes of the drive unit 12 with the primary drive machine ICE alone or with the primary drive machine ICE and the secondary drive machine EM in combination.
  • the primary drive machine ICE can be operated in three fixed gears G2, G5, G6 with torque support from the secondary drive machine EM.
  • Three further "virtual" gears Gl, G3, G4 can be driven with an electrically blocked rotor of the electric machine forming the secondary drive machine EM or with its speed support.
  • the gear change from Gl to G2 takes place for ICE or hybrid operation mode is torque-filled, i.e. without torque interruption
  • the other gear changes occur with torque interruption.
  • the transmission 13 also has three gears El, E2, E3 for EV operation.
  • EV operating modes are operating modes with the secondary drive engine EV alone.
  • the gear changes for EV operation occur with torque interruption.
  • the primary drive machine ICE can be started by the brakes of the secondary drive machine EM. This can also be done when the vehicle battery is low. When the motor vehicle is at a standstill, the primary drive engine can be towed cold - i.e. unfired. A warm - i.e. fired - towing of the primary drive engine ICE can also take place when the motor vehicle is stationary or when the motor vehicle is sailing. Furthermore, it is possible to operate the secondary machine EM as a generator using the primary drive machine ICE when at a standstill - for example to charge the vehicle battery SC.
  • the transmission 13 has a completely progressive gear ratio.
  • the gear ratios between the first gear Gl and the second gear G2, between the third gear G3 and the fifth gear G5 and between the fourth gear G4 and the sixth gear G6 are the same and are each provided by the same pair of gears 1/2, 3/5, 4/6 formed.
  • the three gear pairs 1/2, 3/5, 4/6 are arranged in three parallel gear levels E 2 , ES, £6 of the gear 13.
  • the three switching elements CI, C2, C3 can be designed as simple claw clutches with switching sleeves. This means that the transmission 13 works completely without friction clutches.
  • FIG 2, 3 and 4 show embodiment variants of drive units 11 according to the invention, which are particularly suitable for single-track motor vehicles - in particular motorcycles 11.
  • a parking lock device and a reverse gear can generally be dispensed with.
  • Fig. 5 shows an embodiment variant in which the primary drive machine ICE is arranged coaxially with the secondary drive machine EM.
  • the gears of the gear arrangement 20, at least the gear pairs 3/5 and 4/6 have straight teeth.
  • the planetary gear set PGS is arranged between the gear pair arrangement 20 and the secondary drive machine EM.
  • the primary drive machine ICE is drive-connected to the first link PI of the planetary gear set PGS via a primary drive PD formed, for example, by a gear stage and a torsional vibration damper D. All gears can be designed with straight teeth so that no axial forces occur.
  • the input shaft 14 is connected in a rotationally fixed manner to the third link P3 of the planetary gear set PGS, which is formed by a planet carrier.
  • the first switching element CI locks the planetary gear set PGS in the second switching position R on the right in FIG. 2 by connecting the first link PI - here formed as a ring gear - to the third link P3 in a rotationally fixed manner.
  • the transmission 13 has the following switching pattern in the first embodiment variant shown in FIG. 2 (and in the third embodiment variant shown in FIG. 4):
  • the gear levels 85 and 86 of the gear pairs 3/5 and 4/6 are swapped compared to the first embodiment variant.
  • the gear pair arrangement 20 corresponds to the second embodiment variant.
  • the planetary gear set PGS is arranged concentrically to the primary drive machine ICE and to the secondary drive machine EM, the axis Pa of the planetary gear set PGS being offset with respect to the input shaft 14, i.e. parallel and at a distance from the input shaft 14.
  • the primary drive PD formed by a gear stage, connects the third link P3 of the planetary gear set PGS - here designed as a planet carrier - with the input shaft 14 of the switchable gear pair arrangement 20 of the transmission 13.
  • the first switching element CI blocks the planetary gear set PGS in the - left in Fig. 4 - first switching position L by connecting the first link PI - here designed as a ring gear - with the second link P2 of the planetary gear set PGS - here designed as a sun gear.
  • FIG. 5 shows embodiment variants of drive units 11 according to the invention, which are particularly suitable for multi-lane motor vehicles - especially passenger cars.
  • the drive unit 12 for a multi-lane motor vehicle, in particular a parking lock device and a reversing function are provided.
  • These embodiment variants are particularly advantageous for passenger vehicles with front-wheel drive, with the drive unit 12 being installed transversely, for example.
  • Reference numeral 30 denotes a differential in each of the two fourth, fifth and sixth embodiment variants, which is connected to the final drive FD of the transmission 13.
  • FIG. 6 there is a parking lock wheel P on the first intermediate shaft 16, in the sixth embodiment variant shown in FIG a parking lock device and an idler gear RL of a reverse gear stage RS.
  • a reverse gear GR with torque filling during the switching process can be achieved via the reverse gear stage RS.
  • the first intermediate shaft 16 is drive-connected to the differential 30 via a first final drive FD1 and the second intermediate shaft 160 via a second final drive FD2.
  • the secondary drive machine EM is designed as a high-speed offset electric machine and is drive-connected to the second link P2 of the planetary gear set PGS, which is designed, for example, as a sun gear, via a secondary drive SD - designed, for example, as a spur gear.
  • the gear pairs 1/2, 3/5, 4/6 of the gear pair arrangement 20 are designed as helical teeth.
  • the axial forces do not allow the switching elements to be designed as sliding wheels.
  • the switching elements CI, C2, C3 are therefore designed as switching sleeves.
  • the first switching element CI locks the planetary gear set PGS in the first switching position L - on the left in FIGS. 5, 6, 7 - by connecting the first link PI, designed as a ring gear, to the second link P2, designed as a sun gear.
  • the first switching element CI locks the primary drive machine ICE by connecting the first link PI to the housing H.
  • the second C2 and third switching elements C3 are designed as double switching sleeves, which are arranged axially displaceably in the space between the idler gears 2L and 6L or 5L and RL.
  • Reference number 28 denotes a friction torque limiter.
  • FIG. 6 shows, as a fifth embodiment, a variation of the fourth embodiment with a secondary drive machine EM arranged coaxially to the planetary gear set PGS and to the primary drive machine ICE.
  • the transmission 13 has the following switching pattern in the fourth embodiment variant shown in FIG. 5 and in the fifth embodiment variant shown in FIG. 6: Stationary modes:
  • a sixth embodiment variant is shown as further variations of the fourth embodiment variant.
  • the transmission 13 has a first intermediate shaft 16 and a second intermediate shaft 160.
  • the first switching element CI is - unlike the fourth embodiment variant - arranged in the area of the end of the input shaft 14 facing away from the planetary gear set PGS and thus shifted to the rear of the transmission 13 facing away from the drive side.
  • the drive shaft 15 of the primary drive machine ICE which is non-rotatably connected to the first link PI of the planetary gear set PGS, is guided by the hollow input shaft 14 which is non-rotatably connected to the third link P3 - the planet carrier - of the planetary gear set PGS.
  • the first switching element CI is therefore shifted to the rear side S2 of the transmission 13 facing away from the drive side S1 and optionally connects the inner drive shaft 15 with the hollow input shaft 14 - and thus with the planet carrier P3 (in the right-hand side in FIG. 7) second switching position R ( right position) or in the first switching position L - left in FIG. 7 - the drive shaft 15 with the housing H.
  • the secondary drive machine EM is also designed here as a high-speed offset electric machine, which is connected to the second link P2 - the sun gear - of the planetary gear set PGS via a secondary drive SD designed, for example, as a spur gear stage, the secondary drive SD being arranged in the vicinity of the torsional vibration damper D, whereby the offset electric machine can be designed with the greatest possible axial extension.
  • the parking lock wheel P of a parking lock device is arranged on the second intermediate shaft 160.
  • the parking lock wheel P lies here in the same plane EP as the first switching element CI.
  • the idler gear RL of the reverse gear stage RS is arranged on the second intermediate shaft 160 and meshes with the idler gear 2L of the gear pair 1/2.
  • the idler gear 5L of the gear pair 3/5, which is rotatably arranged on the second intermediate shaft 160, and the idler gear 6L of the gear pair 4/6, which is rotatably arranged on the first intermediate shaft 16, are in engagement with a common fixed gear 5F, 6F on the input shaft 14.
  • the two idler gears 5L and RL can either be activated or deactivated via the second switching element C2. In the neutral position N of the second switching element C2, which corresponds to a middle position, both idler gears 5L and RL are deactivated, i.e. separated from the second intermediate shaft 160.
  • the drive unit 12 in the sixth embodiment variant has - compared to the fourth embodiment variant - a much shorter axial extension and a reduced number of gears.
  • Gears G5 and G6 provide high-efficiency travel gear ratios. No torque support from the secondary drive machine EM is required, as is the case with gears Gl, G3 and G4.
  • An energy-efficient start of the ICE primary drive engine can be carried out even when the battery charge level is low.
  • the secondary drive machine EM is operated in generator mode;
  • the secondary drive machine EM with an output of 10..15% of the ICE power enables the full range of functions (cold/warm towing, starting the primary drive machine ICE, boost/regenerative braking, EV driving in traffic jams);
  • the primary drive machine ICE is connected to the ring gear of the planetary gear set PGS, so that the switching process G1-G2 can take place with active torque filling ATF (positive torque of the secondary drive machine EM, positive speed of the secondary drive machine EM during the switching process, battery is charged and/or electrical energy is dissipated).
  • ATF active torque filling

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Abstract

The invention relates to a drive unit (12) for a motor vehicle, comprising a primary drive machine (ICE), a secondary drive machine (EM) and a transmission (13) having a planetary gear set (PGS) and a gear pair arrangement (20) with a plurality of gear pairs, wherein each gear pair (1/2, 3/5, 4/6) comprises an idler gear (2L, 5L, 6L) which is switchable via a second (C2) or third switching element (C3), and a fixed gear (2F, 5F, 6F). Two members (P1, P3) of the planetary gear set (PGS) can be interconnected for conjoint rotation via a first switching element (C1L) and the primary drive machine (ICE) and/or an input shaft (15) can be connected to a housing (H) of the transmission (13). In at least two gear pairs (1/2, 3/5, 4/6) having the gear ratios iG2, iG5, iG6, the idler gears (2L, 5L, 6L) are rotatably mounted on a first intermediate shaft (16) and the fixed gears (2L, 5L, 6L) are non-rotatably disposed on the input shaft (14). Here, the following applies: i1PGS> 1, where i1pGs is a gear ratio of the planetary gear set (PGS) of the second input shaft (15) to the first input shaft (14) when the secondary drive machine (EM) is stopped, · the gear ratios iG2, iG5, iG6, i1pGs satisfy at least one of the following inequalities: Formula (I).

Description

Antriebseinheit für ein Kraftfahrzeug Drive unit for a motor vehicle
Die Erfindung betrifft eine Antriebseinheit für ein Kraftfahrzeug, insbesondere für ein Motorrad, mit einer Primärantriebsmaschine, einer Sekundärantriebsmaschine und einem Getriebe, welche Antriebseinheit aufweist: The invention relates to a drive unit for a motor vehicle, in particular for a motorcycle, with a primary drive machine, a secondary drive machine and a transmission, which drive unit has:
• eine erste Eingangswelle; • a first input wave;
• eine Ausgangswelle; • an output shaft;
• einer ersten Zwischenwelle, die parallel zur Eingangswelle angeordnet und mit der Ausgangswelle verbunden ist; • a first intermediate shaft arranged parallel to the input shaft and connected to the output shaft;
• einen Planetenradsatz mit einem ersten, zweiten und dritten Glied, wobei das erste Glied mit der Primärantriebsmaschine, das zweite Glied mit der Sekundärantriebsmaschine und das dritte Glied mit der ersten Eingangswelle verbunden sind; • a planetary gear set having first, second and third links, the first link being connected to the primary drive machine, the second link being connected to the secondary drive machine and the third link being connected to the first input shaft;
• zumindest ein erstes Schaltelement, welches ausgebildet ist, um in einer Schaltstellung zwei Glieder des Planetenradsatzes miteinander drehfest zu verbinden und in einer weiteren Schaltstellung die Antriebsmaschine mit dem Gehäuse zu verbinden und zu blockieren; • at least one first switching element, which is designed to connect two members of the planetary gear set to one another in a rotationally fixed manner in a switching position and to connect and block the drive machine with the housing in a further switching position;
• einer Zahnradpaaranordnung mit mehreren Zahnradpaaren, wobei jedes Zahnradpaar ein Festrad und ein Losrad aufweist, wobei jedes Losrad über ein Schaltelement aktivier- oder deaktivierbar ist, wobei • a gear pair arrangement with several pairs of gears, each pair of gears having a fixed gear and an idler gear, each idler gear being able to be activated or deactivated via a switching element, where
• die Zahnradpaare die Übersetzungsverhältnisse IG2, ics, ice aufweisen, und wobei • the gear pairs have the gear ratios IG2, ics, ice, and where
• die Losräder von zumindest zwei Zahnradpaaren auf der Zwischenwelle drehbar gelagert sind, und die Festräder von diesen zumindest zwei Zahnradpaare auf der Eingangswelle drehfest angeordnet sind. • the idler gears of at least two pairs of gears are rotatably mounted on the intermediate shaft, and the fixed gears of these at least two pairs of gears are arranged in a rotationally fixed manner on the input shaft.
Weiters betrifft die Erfindung ein Kraftfahrzeug, insbesondere ein Motorrad, mit einer solchen Antriebseinheit. The invention further relates to a motor vehicle, in particular a motorcycle, with such a drive unit.
Die WO 00/20243 Al offenbart eine Antriebseinheit mit einer Brennkraftmaschine, einer elektrischen Maschine, einem Getriebe mit einer Eingangswelle und einer Zwischenwelle sowie einem Planetengetriebe. Das Getriebe weist eine Zahnradpaaranordnung mit mehreren Zahnradpaaren auf, wobei Festräder der Zahnradpaaranordnungen auf der Eingangswelle und Losräder auf der Zwischenwelle angeordnet sind. Die Losräder sind über Schaltelemente schaltbar. WO 00/20243 A1 discloses a drive unit with an internal combustion engine, an electric machine, a transmission with an input shaft and an intermediate shaft and a planetary gear. The transmission has a gear pair arrangement with several pairs of gears, with fixed gears Gear pair arrangements are arranged on the input shaft and idler gears on the intermediate shaft. The idler gears can be switched via switching elements.
Aus der EP 0 845 618 A2 ist eine ähnliche Antriebseinheit mit einerFrom EP 0 845 618 A2 there is a similar drive unit with a
Getriebeanordnung mit einer Brennkraftmaschine und einer elektrischen Maschine bekannt, welche Getriebeanordnung ein Zahnräderwechselgetriebe, ein Planetengetriebe und zwei Getriebeeingangswellen aufweist, welche über das Planetengetriebe mit einem der elektrischen Maschine verbunden sind. Transmission arrangement with an internal combustion engine and an electric machine is known, which transmission arrangement has a gear change transmission, a planetary gear and two transmission input shafts, which are connected to one of the electric machine via the planetary gear.
Aufgabe der Erfindung ist es, eine kompakte Antriebseinheit mit hohem Schaltkomfort bereitzustellen. The object of the invention is to provide a compact drive unit with a high level of switching comfort.
Die Aufgabe wird mit einem Getriebe der eingangs genannten Art erfindungsgemäß dadurch gelöst, dass gilt: ilPGS> 1, wobei iiPGs ein Übersetzungsverhältnis des Planetenradsatzes (PGS) von dem ersten Glied (PI) zur Eingangswelle (14) mit angehaltener Sekundärantriebsmaschine (EM) ist, und dass die Übersetzungsverhältnisse IG2, ics, iG6, IIPGS mindestens eine der folgenden Ungleichungen erfüllen:
Figure imgf000004_0001
The object is achieved according to the invention with a transmission of the type mentioned in that the following applies: ilPGS> 1, where iiPGs is a transmission ratio of the planetary gear set (PGS) from the first link (PI) to the input shaft (14) with the secondary drive machine (EM) stopped, and that the gear ratios IG2, ics, iG6, IIPGS satisfy at least one of the following inequalities:
Figure imgf000004_0001
Besonders vorteilhaft ist es, wenn das Getriebe eine progressive Gangabstufung aufweist, wobei für die Übersetzungen iGi, iG2, iG3, iG4, ics, ie gilt:
Figure imgf000004_0002
It is particularly advantageous if the transmission has a progressive gear ratio, whereby the following applies to the ratios i G i, iG2, iG3, iG4, ics, ie:
Figure imgf000004_0002
Günstigerweise ist vorgesehen, dass für die Übersetzungen iiPGs, IGI, iG2 gilt:
Figure imgf000004_0003
In einer vorteilhaften Ausführung der Erfindung ist vorgesehen, dass das erste Glied des Planetenradsatzes als Hohlrad, das zweite Glied des Planetenradsatzes als Sonnenrad und das dritte Glied des Planetenradsatzes als Steg ausgebildet ist. Conveniently it is provided that the following applies to the translations ii PG s, IGI, iG2:
Figure imgf000004_0003
In an advantageous embodiment of the invention it is provided that the first member of the planetary gear set is designed as a ring gear, the second member of the planetary gear set is designed as a sun gear and the third member of the planetary gear set is designed as a web.
Dabei gilt bevorzugt: The following applies preferably:
. _ z1+z2 . _ z 1+ z 2
1PGS~ z2 ' wobei zi die Anzahl der Zähne desSonnenrades und Z2 die Anzahl der Zähne des Hohlrades ist. 1PGS~ z 2 ' where zi is the number of teeth of the sun gear and Z2 is the number of teeth of the ring gear.
In einigen erfindungsgemäßen Ausführungsvarianten ist vorgesehen, dass das Losrad eines Zahnradpaares auf der Eingangswelle drehbar gelagert ist, und das Festrad dieses Zahnradpaares auf der ersten Zwischenwelle drehfest angeordnet ist. Dabei kann der Planetenradsatz zwischen der Zahnradpaaranordnung und der Sekundärantriebsmaschine angeordnet sein. Vorzugsweise ist die Sekundärantriebsmaschine koaxial mit dem Planetenradsatz angeordnet. In einer besonders kompakten Ausführungsvariante der Erfindung ist vorgesehen, dass die Primärantriebsmaschine koaxial mit dem Planetenradsatz und der Sekundärantriebsmaschine und distanziert zur Eingangswelle angeordnet ist. In some embodiment variants according to the invention it is provided that the idler gear of a gear pair is rotatably mounted on the input shaft, and the fixed gear of this gear pair is arranged in a rotationally fixed manner on the first intermediate shaft. The planetary gear set can be arranged between the gear pair arrangement and the secondary drive machine. Preferably, the secondary drive machine is arranged coaxially with the planetary gear set. In a particularly compact embodiment variant of the invention it is provided that the primary drive machine is arranged coaxially with the planetary gear set and the secondary drive machine and at a distance from the input shaft.
Eine weitere Ausführungsvariante der Erfindung sieht vor, dass das Losrad eines Zahnradpaares auf der ersten Zwischenwelle und das Losrad eines anderen Zahnradpaares auf einer zweiten Zwischenwelle drehbar gelagert ist, wobei die beiden Losräder mit einem gemeinsamen Festrad auf der Eingangswelle im Zahneingriff stehen. Die beiden Zahnradpaare teilen sich somit ein gemeinsames Festrad. Dadurch können Bauteile und Bauraum eingespart werden. A further embodiment variant of the invention provides that the idler gear of a pair of gears is rotatably mounted on the first intermediate shaft and the idler gear of another pair of gears is rotatably mounted on a second intermediate shaft, the two idler gears meshing with a common fixed gear on the input shaft. The two pairs of gears therefore share a common fixed gear. This allows components and installation space to be saved.
Bei anderen erfindungsgemäßen Ausführungsvarianten ist vorgesehen, dass die Losräder von zumindest drei Zahnradpaaren auf der Zwischenwelle drehbar gelagert sind, und die Festräder von diesen zumindest drei Zahnradpaare auf der Eingangswelle drehfest angeordnet sind, wobei vorzugsweise das Losrad von einer Rückwärtsgangzahnradstufe auf einer Zwischenwelle, vorzugsweise der ersten Zwischenwelle, drehbar gelagert ist. Insbesondere bei letzteren Ausführungsvarianten kann vorgesehen sein, dass die Primärantriebsmaschine koaxial mit dem Planetenradsatz und die Sekundärantriebsmaschine parallel und distanziert zur Eingangswelle angeordnet ist. In einer alternativen Ausführung ist im Rahmen der Erfindung vorgesehen, dass die Primärantriebsmaschine koaxial mit der Sekundärantriebsmaschine angeordnet. In other embodiment variants according to the invention, it is provided that the idler gears of at least three pairs of gears are rotatably mounted on the intermediate shaft, and the fixed gears of these at least three pairs of gears are arranged in a rotationally fixed manner on the input shaft, preferably the idler gear of a reverse gear stage on an intermediate shaft, preferably the first Intermediate shaft, is rotatably mounted. Particularly in the latter embodiment variants, it can be provided that the primary drive machine is arranged coaxially with the planetary gear set and the secondary drive machine is arranged parallel and at a distance from the input shaft. In an alternative embodiment, the invention provides that the primary drive machine is arranged coaxially with the secondary drive machine.
In Ausführungen für Motorräder kann jeweils auf eine Parksperrvorrichtung verzichtet werden. Bei Anwendungen für Kraftfahrzeuge ist es vorteilhaft, wenn die Antriebseinheit eine Parksperrvorrichtung mit zumindest einem sperrbaren Parksperrenrad aufweist, wobei das Parksperrenrad auf der ersten Zwischenwelle oder der zweiten Zwischenwelle angeordnet ist. In versions for motorcycles, a parking lock device can be dispensed with. In applications for motor vehicles, it is advantageous if the drive unit has a parking lock device with at least one lockable parking lock wheel, the parking lock wheel being arranged on the first intermediate shaft or the second intermediate shaft.
In einer äußerst kompakten Ausführungsvariante der Erfindung ist vorgesehen, dass zumindest ein Schaltelement durch eine axial verschiebbare Schalthülse, vorzugsweise eine axial verschiebbare Doppelschalthülse, gebildet ist. Zumindest ein Schaltelement weist günstigerweise zwei Schaltstellungen und vorzugsweise zwischen einer ersten und einer zweiten Schaltstellung eine Neutralstellung auf. In an extremely compact embodiment variant of the invention it is provided that at least one switching element is formed by an axially displaceable switching sleeve, preferably an axially displaceable double switching sleeve. At least one switching element advantageously has two switching positions and preferably a neutral position between a first and a second switching position.
Durch das zweite oder dritte Schaltelement können die Losräder von Zahnradpaaren geschaltet, also aktiviert bzw. deaktiviert werden. Dabei ist bei Schaltelementen mit Doppelschalthülse in jeder der Schaltstellungen zumindest ein Losrad aktiviert und das andere deaktiviert. In der Neutralstellung sind beide Losräder der benachbarten Zahnradpaare deaktiviert. Aktiviert bedeutet dabei, dass das Losrad mit der Zwischenwelle drehfest verbunden wird. Deaktiviert bedeutet, dass das entsprechende Losrad von der Zwischenwelle entkoppelt wird, also auf dieser frei drehbar ist. The idler gears of gear pairs can be switched, i.e. activated or deactivated, by the second or third switching element. In the case of switching elements with a double switching sleeve, at least one idler gear is activated and the other is deactivated in each of the switching positions. In the neutral position, both idler gears of the neighboring gear pairs are deactivated. Activated means that the idler gear is connected to the intermediate shaft in a rotation-proof manner. Deactivated means that the corresponding idler gear is decoupled from the intermediate shaft, i.e. it can rotate freely on it.
Besonders vorteilhaft ist es, wenn das erste Schaltelement einstückig mit einem Festrad zumindest eines benachbarten Zahnradpaares ausgebildet ist. Dadurch kann Bauraum und die Teileanzahl gespart werden. Das Festrad wird beim Schaltvorgang mit dem ersten Schaltelement axial mitverschoben. Diese Ausführung bedingt eine Gradverzahnung der Zahnräder des betroffenen Zahnradpaares. It is particularly advantageous if the first switching element is designed in one piece with a fixed gear of at least one adjacent pair of gears. This allows installation space and the number of parts to be saved. The fixed gear is moved axially with the first switching element during the switching process. This design requires degree gearing of the gears of the affected gear pair.
Günstigerweise ist die Primärantriebsmaschine durch eine Brennkraftmaschine und die Sekundärantriebsmaschine durch eine elektrische Maschine gebildet. Die Aufgabe kann weiters mit einem Kraftfahrzeug, beispielsweise einem Motorrad, mit einer Antriebseinheit gelöst werden, bei der erfindungsgemäß das Getriebe ausgebildet ist, um zumindest einen Gangwechsel - vorzugsweise vom ersten in den zweiten Gang - mit aktiver Drehmomentauffüllung durch die Sekundärantriebsmaschine durchzuführen. Dadurch kann der Schaltkomfort von Schaltvorgängen wesentlich verbessert werden. The primary drive machine is advantageously formed by an internal combustion engine and the secondary drive machine by an electrical machine. The object can further be achieved with a motor vehicle, for example a motorcycle, with a drive unit in which, according to the invention, the transmission is designed to carry out at least one gear change - preferably from first to second gear - with active torque replenishment by the secondary drive machine. As a result, the comfort of switching operations can be significantly improved.
Die Erfindung wird im Folgenden anhand der in den Figuren gezeigten nicht einschränkenden Ausführungsbeispielen näher erläutert. Darin zeigen schematisch: The invention is explained in more detail below using the non-limiting exemplary embodiments shown in the figures. It shows schematically:
Fig. 1 ein Kraftfahrzeug mit einer erfindungsgemäßen Antriebseinheit; 1 shows a motor vehicle with a drive unit according to the invention;
Fig. 2 eine erfindungsgemäße Antriebseinheit in einer ersten Ausführungsvariante; 2 shows a drive unit according to the invention in a first embodiment variant;
Fig. 3 eine erfindungsgemäße Antriebseinheit in einer zweiten Ausführungsvariante; 3 shows a drive unit according to the invention in a second embodiment variant;
Fig. 4 eine erfindungsgemäße Antriebseinheit in einer dritten Ausführungsvariante; 4 shows a drive unit according to the invention in a third embodiment variant;
Fig. 5 eine erfindungsgemäße Antriebseinheit in einer vierten Ausführungsvariante; 5 shows a drive unit according to the invention in a fourth embodiment variant;
Fig. 6 eine erfindungsgemäße Antriebseinheit in einer fünften Ausführungsvariante; 6 shows a drive unit according to the invention in a fifth embodiment variant;
Fig. 7 eine erfindungsgemäße Antriebseinheit in einer sechsten Ausführungsvariante; und 7 shows a drive unit according to the invention in a sixth embodiment variant; and
Fig. 8 ein Gangwechselkennfeld der erfindungsgemäßen Antriebseinheit. Fig. 8 shows a gear change map of the drive unit according to the invention.
Fig. 1 zeigt ein Motorrad 11 mit einem erfindungsgemäßen Antriebseinheit 12, bestehend aus einer Primärantriebsmaschine ICE, eine Sekundärantriebsmaschine EM und einem Getriebe 13 mit quer angeordneten parallelen Eingangs- 14, Zwischen- 16 und Ausgangswellen 17. Die Ausgangswelle 17 ist über einen im dargestellten Ausführungsbeispiel durch ein Zugmittelgetriebe gebildeten Finaltrieb FD beispielsweise über eine Antriebskette 18 mit einem Hinterrad 19 des Motorrades 1 antriebsverbunden. Die Primärantriebsmaschine ICE ist in den Ausführungsbeispielen durch eine Brennkraftmaschine und die Sekundärantriebseinheit EM durch eine elektrische Maschine gebildet. Fig. 1 shows a motorcycle 11 with a drive unit 12 according to the invention, consisting of a primary drive machine ICE, a secondary drive machine EM and a transmission 13 with transversely arranged parallel input 14, intermediate 16 and output shafts 17. The output shaft 17 is via one in the exemplary embodiment shown Final drive formed by a traction mechanism FD, for example, is drive-connected to a rear wheel 19 of the motorcycle 1 via a drive chain 18. In the exemplary embodiments, the primary drive machine ICE is formed by an internal combustion engine and the secondary drive unit EM by an electric machine.
In Fig. 2 ist die Antriebseinheit 12 aus Fig. 1 im Detail dargestellt. Das Getriebe 13 der Antriebseinheit 12 ist in jeder der Ausführungsvarianten ausgebildet, um zumindest zwei Gangwechsel mit aktiver Drehmomentstützung durch die Sekundärantriebsmaschine EM durchzuführen. In Fig. 2, the drive unit 12 from Fig. 1 is shown in detail. The transmission 13 of the drive unit 12 is designed in each of the embodiment variants to carry out at least two gear changes with active torque support by the secondary drive machine EM.
Das Getriebe 13 weist eine Eingangswelle 14 auf. Die Ausgangswelle 17 ist mit der einer ersten Zwischenwelle 16 drehfest verbunden oder mit dieser einstückig ausgeführt. Die erste Zwischenwelle 16 ist parallel zu der Eingangswelle 14 angeordnet. Das Getriebe 13 weist einen Planetenradsatz PGS mit einem ersten PI, zweiten P2 und dritten Glied P3 auf, wobei das erste Glied PI mit der Primärantriebsmaschine ICE, das zweite Glied P2 mit der Sekundärantriebsmaschine EM und das dritte Glied P3 mit der Eingangswelle 14 verbunden sind. Im in Fig. 2 gezeigten ersten Ausführungsbeispiel ist die Primärantriebsmaschine über einen durch eine Stirnradstufe gebildeten Primärtrieb PD mit dem ersten Glied PI des Planetenradsatzes PGS antriebsverbunden. The transmission 13 has an input shaft 14. The output shaft 17 is connected in a rotationally fixed manner to a first intermediate shaft 16 or is designed in one piece with it. The first intermediate shaft 16 is arranged parallel to the input shaft 14. The transmission 13 has a planetary gear set PGS with a first PI, second P2 and third link P3, the first link PI being connected to the primary drive machine ICE, the second link P2 to the secondary drive machine EM and the third link P3 to the input shaft 14. In the first exemplary embodiment shown in FIG. 2, the primary drive machine is drive-connected to the first member PI of the planetary gear set PGS via a primary drive PD formed by a spur gear stage.
Das Getriebe 13 weist eine Zahnradpaaranordnung 20 mit drei Zahnradpaaren 1/2, 3/5, 4/6, wobei jedes Zahnradpaar 1/2, 3/5, 4/6, ein Festrad 2F, 5F, 6F und ein Losrad 2L, 5L, 6L aufweist, welche miteinander korrespondieren und im Zahneingriff stehen. Festräder sind Zahnräder, welche drehfest mit der jeweils tragenden Welle - beispielsweise der Eingangswelle 14 oder der ersten Zwischenwelle 16 - verbunden sind. Losräder sind Zahnräder, welche drehbar auf der tragenden Welle - der ersten Zwischenwelle 16 oder der Eingangswelle 14 - gelagert sind. Das Losrad 2L, 5L, 6L und das Festrad 2F, 5F, 6F jedes Zahnradpaares 1/2, 3/5, 4/6 sind also auf verschiedenen tragenden Wellen angeordnet, wobei die tragenden Wellen parallel und voneinander beabstandet im Getriebe 13 angeordnet sind. The transmission 13 has a gear pair arrangement 20 with three gear pairs 1/2, 3/5, 4/6, each gear pair 1/2, 3/5, 4/6, a fixed gear 2F, 5F, 6F and an idler gear 2L, 5L , 6L, which correspond to each other and are in tooth mesh. Fixed gears are gears that are connected in a rotationally fixed manner to the respective supporting shaft - for example the input shaft 14 or the first intermediate shaft 16. Idler gears are gears that are rotatably mounted on the supporting shaft - the first intermediate shaft 16 or the input shaft 14. The idler gear 2L, 5L, 6L and the fixed gear 2F, 5F, 6F of each gear pair 1/2, 3/5, 4/6 are therefore arranged on different supporting shafts, the supporting shafts being arranged parallel and spaced apart from one another in the gear 13.
Die Losräder 2L, 6L der Zahnradpaare 1/2, 4/6 sind auf der ersten Zwischenwelle 16 drehbar angeordnet. Zwei jeweils durch ein Festrad 2F, 6F gebildete Zahnräder von zwei Zahnradpaaren 1/2, 4/6 sind auf und drehfest mit der Eingangswelle 14 angeordnet. Das Losrad L5 des Zahnradpaares 3/5 ist auf der Eingangswelle 14 drehbar angeordnet. Das Festrad F5 des Zahnradpaares 3/5 ist auf und drehfest mit der ersten Zwischenwelle 16 angeordnet. The idler gears 2L, 6L of the gear pairs 1/2, 4/6 are rotatably arranged on the first intermediate shaft 16. Two gears of two pairs of gears 1/2, 4/6, each formed by a fixed gear 2F, 6F, are arranged on and non-rotatably with the input shaft 14. The idler gear L5 of the gear pair 3/5 is on the input shaft 14 rotatably arranged. The fixed gear F5 of the gear pair 3/5 is arranged on and non-rotatably with the first intermediate shaft 16.
Zu Durchführung von Gangwechseln sind ein erstes Schaltelement CI, ein zweites Schaltelement C2 und ein drittes Schaltelement C3 vorgesehen. To carry out gear changes, a first switching element CI, a second switching element C2 and a third switching element C3 are provided.
Jedes der als Schalthülse ausgebildeten Schaltelemente CI, C2, C3 weist zwei Schaltstellungen auf. Das erste CI und dritte Schaltelement C3 ist als Doppelschalthülse ausgebildet und weist zwischen den beiden Schaltstellungen zusätzlich noch eine Neutralstellung N auf. Each of the switching elements CI, C2, C3 designed as a switching sleeve has two switching positions. The first CI and third switching element C3 is designed as a double switching sleeve and also has a neutral position N between the two switching positions.
Das erste Schaltelement CI blockiert in der ersten Schaltstellung L - in Fig. 2 der linken Schaltstellung - die Primärantriebsmaschine ICE indem eine Drehverbindung mit dem Gehäuse H hergestellt wird. In der zweiten - in Fig. 2 rechten - Schaltstellung R werden das erste Glied PI und das dritte Glied P3 des Planetenradsatzes PGS drehfest miteinander gekoppelt. In der Neutralstellung N ist die drehfeste Verbindung mit dem Gehäuse H oder zwischen den beiden Gliedern PI und P3 aufgehoben. The first switching element CI blocks the primary drive machine ICE in the first switching position L - the left switching position in FIG. 2 - by establishing a rotary connection with the housing H. In the second switching position R - right in FIG. 2 - the first link PI and the third link P3 of the planetary gear set PGS are coupled to one another in a rotationally fixed manner. In the neutral position N, the non-rotatable connection with the housing H or between the two members PI and P3 is canceled.
Das zweite Schaltelement C2 dient bei der in Fig. 2 dargestellten ersten Ausführungsvariante zum Aktivieren oder Deaktivieren des Losrades L5 des Zahnradpaares 3/5. Die Schalthülse des zweiten Schaltelements C2 ist mit dem Festrad 6F des Zahnradpaares 4/6 fest verbunden oder einstückig mit diesem ausgebildet. In der ersten - in Fig. 2 linken - Schaltstellung L des zweiten Schaltelementes C2 ist das Losrad L5 deaktiviert, also von der Eingangswelle 14 getrennt. In der zweiten - in Fig. 2 rechten Schaltstellung R des zweiten Schaltelementes C2 ist das Losrad L5 aktiviert, also drehfest mit der Eingangswelle 14 verbunden. The second switching element C2 is used in the first embodiment variant shown in FIG. 2 to activate or deactivate the idler gear L5 of the gear pair 3/5. The switching sleeve of the second switching element C2 is firmly connected to the fixed gear 6F of the gear pair 4/6 or is formed in one piece with it. In the first - left in FIG. 2 - switching position L of the second switching element C2, the idler gear L5 is deactivated, i.e. separated from the input shaft 14. In the second - right in Fig. 2 switching position R of the second switching element C2, the idler gear L5 is activated, i.e. connected to the input shaft 14 in a rotationally fixed manner.
Das dritte Schaltelement C3 dient zum Aktivieren oder Deaktivieren des Losrades L6 des Zahnradpaares 4/6 und des Losrades L2 des Zahnradpaares 1/2. In der ersten - in Fig. 2 linken - Schaltstellung des dritten Schaltelementes C3 ist das Losrad L6 aktiviert, also mit der ersten Zwischenwelle 16 drehfest verbunden, und das Losrad L2 deaktiviert, also von der ersten Zwischenwelle 16 getrennt. In der zweiten - in Fig. 2 rechten Schaltstellung des zweiten Schaltelementes C3 ist das Losrad L6 aktiviert, also drehfest mit der ersten Zwischenwelle 16 verbunden und das Losrad L2 deaktiviert, also von der ersten Zwischenwelle 16 getrennt. In der Neutralstellung N des dritten Schaltelementes C3 ist die drehfeste Verbindung zwischen den Losrädern L6 und L2 mit der ersten Zwischenwelle 16 unterbrochen, die Losräder 6L und 2L sind frei auf der tragenden ersten Zwischenwelle 16 drehbar. The third switching element C3 is used to activate or deactivate the idler gear L6 of the gear pair 4/6 and the idler gear L2 of the gear pair 1/2. In the first - left in FIG. In the second switching position of the second switching element C3 - right in FIG. In the Neutral position N of the third switching element C3, the rotationally fixed connection between the idler gears L6 and L2 with the first intermediate shaft 16 is interrupted, the idler gears 6L and 2L are freely rotatable on the supporting first intermediate shaft 16.
Die Zahnräder auf der Eingangswelle 14 weisen mit den Zahnrädern auf der ersten Zwischenwelle 16 Übersetzungsverhältnisse iG2 - für das Zahnradpaar 1/2 ics - für das Zahnradpaar 3/5 - und ice - für das Zahnradpaar 4/6 - auf. The gears on the input shaft 14 have gear ratios iG2 - for the gear pair 1/2 ics - for the gear pair 3/5 - and ice - for the gear pair 4/6 - with the gears on the first intermediate shaft 16.
Mit iiPGs ist ein Übersetzungsverhältnis des Planetenradsatzes PGS von der zweiten Eingangswelle 15 zur ersten Eingangswelle 14 bei angehaltener Sekundärantriebsmaschine EM bezeichnet. Dieses Übersetzungsverhältnis iiPGs ist in allen erfindungsgemäßen Ausführungsvarianten größer als 1 ausgebildet: iiPGs denotes a transmission ratio of the planetary gear set PGS from the second input shaft 15 to the first input shaft 14 when the secondary drive machine EM is stopped. This transmission ratio iiPGs is greater than 1 in all embodiment variants according to the invention:
• i lPGS > 1 (1), • i lPGS > 1 (1),
Weiters ist vorgesehen, dass die Übersetzungsverhältnisse IG2, IG3, IGS, iG6, IIPGS mindestens eine der folgenden Ungleichungen erfüllen:
Figure imgf000010_0001
Furthermore, it is provided that the gear ratios IG2, IG3, IGS, iG6, IIPGS fulfill at least one of the following inequalities:
Figure imgf000010_0001
Das Getriebe 13 weist in allen Ausführungsvarianten der Erfindung eine progressive Gangabstufung der Gänge Gl, G2, G3, G4, G5, G6 auf, wobei für die Übersetzungen iGi, iG2, IG3, iG4, ics, ie gilt:
Figure imgf000010_0002
für die Übersetzungen SIPGS, IGI, iG2 gilt: In all embodiment variants of the invention, the transmission 13 has a progressive gear gradation of the gears Gl, G2, G3, G4, G5, G6, whereby the following applies to the translations i G i, iG2, IG3, iG4, ics, ie:
Figure imgf000010_0002
The following applies to the translations SIPGS, IGI, iG2:
• i = 1PGS 1G2 (5) • i = 1PGS 1 G2 (5)
Fig. 8 zeigt ein Gangwechselkennfeld der erfindungsgemäßen Antriebseinheit 12. Die progressive Gangabstufung ist durch die strichlierten Linien deutlich zu erkennen. In allen in Fig. 2 bis 7 gezeigten Ausführungsvarianten ist das erste Glied PI des Planetenradsatzes PGS als Hohlrad, das zweite Glied P2 des Planetenradsatzes PGS als Sonnenrad und das dritte Glied P3 des Planetenradsatzes PGS als Planetenträger ausgebildet ist. Dabei gilt:
Figure imgf000011_0001
wobei zi die Anzahl der Zähne des Sonnenrades und Z2 die Anzahl der Zähne des Hohlrades ist. Fig. 8 shows a gear change map of the drive unit 12 according to the invention. The progressive gear gradation can be clearly seen by the dashed lines. 2 to 7, the first link PI of the planetary gear set PGS is designed as a ring gear, the second link P2 of the planetary gear set PGS is designed as a sun gear and the third link P3 of the planetary gear set PGS is designed as a planet carrier. The following applies:
Figure imgf000011_0001
where zi is the number of teeth of the sun gear and Z2 is the number of teeth of the ring gear.
Das Getriebe 13 weist insgesamt 6 Gänge Gl, G2, G3, G4, G5, G6 für ICE- oder Hybrid-Betriebsweise auf. ICE- oder Hybrid-Betriebsweisen sind Betriebsweisen der Antriebseinheit 12 mit der Primärantriebsmaschine ICE allein oder mit der Primärantriebsmaschine ICE und der Sekundärantriebsmaschine EM in Kombination. Dabei kann in drei festen Gängen G2, G5, G6 die Primärantriebsmaschine ICE mit Drehmomentunterstützung der Sekundärantriebsmaschine EM betrieben werden. Drei weitere „virtuelle" Gänge Gl, G3, G4 können mit elektrisch blockiertem Rotor der die Sekundärantriebsmaschine EM bildenden elektrischen Maschine oder mit deren Drehzahlunterstützung gefahren werden. Der Gangwechsel von Gl auf G2 erfolgt für ICE- oder Hybrid- Betriebsweise erfolgt drehmomentgefüllt, also ohne Drehmomentunterbrechung. Die anderen Gangwechsel erfolgen mit Drehmomentunterbrechung. The transmission 13 has a total of 6 gears Gl, G2, G3, G4, G5, G6 for ICE or hybrid operation. ICE or hybrid operating modes are operating modes of the drive unit 12 with the primary drive machine ICE alone or with the primary drive machine ICE and the secondary drive machine EM in combination. The primary drive machine ICE can be operated in three fixed gears G2, G5, G6 with torque support from the secondary drive machine EM. Three further "virtual" gears Gl, G3, G4 can be driven with an electrically blocked rotor of the electric machine forming the secondary drive machine EM or with its speed support. The gear change from Gl to G2 takes place for ICE or hybrid operation mode is torque-filled, i.e. without torque interruption The other gear changes occur with torque interruption.
Das Getriebe 13 weist weiters drei Gänge El, E2, E3 für EV- Betriebsweise auf. EV- Betriebsweisen sind Betriebsweisen mit der Sekundärantriebsmaschine EV allein. Die Gangwechsel für EV-Betriebsweise erfolgen mit Drehmomentunterbrechung. The transmission 13 also has three gears El, E2, E3 for EV operation. EV operating modes are operating modes with the secondary drive engine EV alone. The gear changes for EV operation occur with torque interruption.
Ein Start der Primärantriebsmaschine ICE kann durch die Bremsen der Sekundärantriebsmaschine EM erfolgen. Dies kann auch bei niedrigem Ladezustand der Fahrzeugbatterie erfolgen. Im Stillstand des Kraftfahrzeuges kann die Primärantriebsmaschine kalt - also ungefeuert - geschleppt werden. Ein warmes - also gefeuertes - Schleppen der Primärantriebsmaschine ICE kann ebenfalls bei stillstehendem Kraftfahrzeug oder im Segelbetrieb des Kraftfahrzeuges erfolgen. Weiters ist es möglich im Stillstand die Sekundärmaschine EM durch die Primärantriebsmaschine ICE generatorisch - beispielsweise zum Laden SC der Fahrzeugbatterie - zu betreiben. The primary drive machine ICE can be started by the brakes of the secondary drive machine EM. This can also be done when the vehicle battery is low. When the motor vehicle is at a standstill, the primary drive engine can be towed cold - i.e. unfired. A warm - i.e. fired - towing of the primary drive engine ICE can also take place when the motor vehicle is stationary or when the motor vehicle is sailing. Furthermore, it is possible to operate the secondary machine EM as a generator using the primary drive machine ICE when at a standstill - for example to charge the vehicle battery SC.
Vorteilhafterweise weist das Getriebe 13 eine vollständig progressive Gangabstufung auf. Die Übersetzungen zwischen dem ersten Gang Gl und dem zweiten Gang G2, zwischen dem dritten Gang G3 und dem fünften Gang G5 sowie zwischen dem vierten Gang G4 und dem sechsten Gang G6 sind gleich und werden jeweils durch dasselbe Zahnradpaar 1/2, 3/5, 4/6 gebildet. Advantageously, the transmission 13 has a completely progressive gear ratio. The gear ratios between the first gear Gl and the second gear G2, between the third gear G3 and the fifth gear G5 and between the fourth gear G4 and the sixth gear G6 are the same and are each provided by the same pair of gears 1/2, 3/5, 4/6 formed.
Die drei Zahnradpaare 1/2, 3/5, 4/6 sind in drei parallelen Getriebeebenen E2, ES, £6 des Getriebes 13 angeordnet. The three gear pairs 1/2, 3/5, 4/6 are arranged in three parallel gear levels E 2 , ES, £6 of the gear 13.
Die drei Schaltelemente CI, C2, C3 können als einfache Klauenkupplungen mit Schalthülsen ausgeführt sein. Damit kommt das Getriebe 13 völlig ohne Reibungskupplungen aus. The three switching elements CI, C2, C3 can be designed as simple claw clutches with switching sleeves. This means that the transmission 13 works completely without friction clutches.
Die Fig. 2, 3 und 4 zeigen Ausführungsvarianten von erfindungsgemäßen Antriebseinheiten 11, welche besonders für einspurige Kraftfahrzeuge - insbesondere Motorräder 11 - geeignet sind. Bei Anwendung der Antriebseinheit 12 für ein einspuriges Kraftfahrzeug kann im Allgemeinen auf eine Parksperrvorrichtung und auf einen Rückwärtsgang verzichtet werden. 2, 3 and 4 show embodiment variants of drive units 11 according to the invention, which are particularly suitable for single-track motor vehicles - in particular motorcycles 11. When using the drive unit 12 for a single-track motor vehicle, a parking lock device and a reverse gear can generally be dispensed with.
In den Fig. 2 bis 4, 6 und 7 ist jeweils die Sekundärantriebsmaschine EM koaxial mit dem Planetenradsatz PGS angeordnet. Fig. 5 zeigt eine Ausführungsvariante, bei der die Primärantriebsmaschine ICE koaxial mit der Sekundärantriebsmaschine EM angeordnet ist. 2 to 4, 6 and 7, the secondary drive machine EM is arranged coaxially with the planetary gear set PGS. Fig. 5 shows an embodiment variant in which the primary drive machine ICE is arranged coaxially with the secondary drive machine EM.
Bei den in den Fig. 2 bis 4 dargestellten Ausführungsvarianten sind die Zahnräder der Zahnradanordnung 20, zumindest der Zahnradpaare 3/5 und 4/6, gerade verzahnt. Dies ermöglicht es, das zweite Schaltelement C2 und das dritte Schaltelement C3 jeweils durch eine axial verschiebbare Schalthülseneinheit auszubilden, wobei das zweite Schaltelement C2 fest mit einem angrenzenden Festrad 5F des benachbarten Zahnradpaares 3/5, und das dritte Schaltelement C3 fest mit einem angrenzenden Festrad 6F des benachbarten Zahnradpaares 4/6 verbunden, beispielsweise einstückig mit diesen ausgebildet sind. Bei der in Fig. 2 gezeigten ersten Ausführungsvariante ist der Planetenradsatz PGS zwischen der Zahnradpaaranordnung 20 und der Sekundärantriebsmaschine EM angeordnet. Die Primärantriebsmaschine ICE ist über einen beispielsweise durch eine Zahnradstufe gebildeten Primärtrieb PD und einen Drehschwingungsdämpfer D mit dem ersten Glied PI des Planetenradsatzes PGS antriebsverbunden. Alle Zahnräder können geradeverzahnt ausgeführt werden, sodass keine axialen Kräfte auftreten. In the embodiment variants shown in FIGS. 2 to 4, the gears of the gear arrangement 20, at least the gear pairs 3/5 and 4/6, have straight teeth. This makes it possible to form the second switching element C2 and the third switching element C3 each by an axially displaceable switching sleeve unit, the second switching element C2 being firmly connected to an adjacent fixed gear 5F of the adjacent gear pair 3/5, and the third switching element C3 being fixed to an adjacent fixed gear 6F of the adjacent gear pair 4/6 are connected, for example formed in one piece with them. In the first embodiment variant shown in FIG. 2, the planetary gear set PGS is arranged between the gear pair arrangement 20 and the secondary drive machine EM. The primary drive machine ICE is drive-connected to the first link PI of the planetary gear set PGS via a primary drive PD formed, for example, by a gear stage and a torsional vibration damper D. All gears can be designed with straight teeth so that no axial forces occur.
Die Eingangswelle 14, ist mit dem durch einen Planetenträger gebildeten dritten Glied P3 des Planetenradsatzes PGS drehfest verbunden. Das erste Schaltelement CI sperrt den Planetenradsatz PGS in der in Fig. 2 rechten zweiten Schaltstellung R, indem das - hier als Hohlrad gebildete - erste Glied PI mit dem dritten Glied P3 drehfest verbunden wird. The input shaft 14 is connected in a rotationally fixed manner to the third link P3 of the planetary gear set PGS, which is formed by a planet carrier. The first switching element CI locks the planetary gear set PGS in the second switching position R on the right in FIG. 2 by connecting the first link PI - here formed as a ring gear - to the third link P3 in a rotationally fixed manner.
Das Getriebe 13 weist in der in Fig. 2 gezeigten ersten Ausführungsvariante (und in der in Fig. 4 gezeigten dritten Ausführungsvariante) folgendes Schaltschema auf: The transmission 13 has the following switching pattern in the first embodiment variant shown in FIG. 2 (and in the third embodiment variant shown in FIG. 4):
Stationäre Modi :
Figure imgf000013_0001
Stationary modes:
Figure imgf000013_0001
Transiente Modi:
Figure imgf000013_0002
Transient modes:
Figure imgf000013_0002
Figure imgf000014_0001
Figure imgf000014_0001
In der Schalttabelle bedeuten Meaning in the switching table
L Schaltung nach links (bezogen auf Fig. 2 oder Fig. 4)L Shift to the left (related to Fig. 2 or Fig. 4)
R Schaltung nach rechts (bezogen auf Fig. 2 oder Fig. 4)R switching to the right (related to Fig. 2 or Fig. 4)
X aktiviert X activated
NO neutraler Gang NO neutral gear
SC Laden der Fahrzeugbatterie SC Charging the vehicle battery
El erster Gang im EV-Modus El first gear in EV mode
E2 zweiter Gang im EV-Modus E2 second gear in EV mode
Gl erster Gang im ICE- und Hybridmodus Gl first gear in ICE and hybrid mode
G2 zweiter Gang im ICE- und Hybridmodus G2 second gear in ICE and hybrid mode
G3 dritter Gang im ICE- und Hybridmodus G3 third gear in ICE and hybrid mode
G4 vierter Gang im ICE- und Hybridmodus G4 fourth gear in ICE and hybrid mode
G5 fünfter Gang im ICE- und Hybridmodus G5 fifth gear in ICE and hybrid mode
G6 sechster Gang im ICE- und Hybridmodus G6 sixth gear in ICE and hybrid mode
Im Folgenden wird ein konkretes Ausführungsbeispiel der erstenBelow is a concrete exemplary embodiment of the first
Ausführungsvariante gezeigt. Das Getriebe 13 weist folgende Parameter auf: z i = 33 z 2 = 75 G2 = 2.75 i G5 = 1.49 i G6 = 1.24 mit z i Anzahl der Zähne des Sonnenrades des Planetenradsatzes PGS; ' z Anzahl der Zähne des Hohlrades des Planetenradsatzes PGS; iG2 Übersetzungsverhältnis für das Zahnradpaar 1/2; iG5 Übersetzungsverhältnis für das Zahnradpaar 3/5; i Übersetzungsverhältnis für das Zahnradpaar 4/6. 1.44
Figure imgf000015_0001
i Gl = i G2 i 1PGS = 3.96 iG3 = iG5 i lPGS = 2.15 i G4 = i G6 i 1PGS = 1.79 Version shown. The transmission 13 has the following parameters: zi = 33 z 2 = 75 G2 = 2.75 i G5 = 1.49 i G6 = 1.24 with zi Number of teeth of the sun gear of the planetary gear set PGS; ' z number of teeth of the ring gear of the planetary gear set PGS; i G2 gear ratio for the gear pair 1/2; i G5 gear ratio for the gear pair 3/5; i Gear ratio for the gear pair 4/6. 1.44
Figure imgf000015_0001
i Eq = i G2 i 1PGS = 3.96 iG3 = iG5 i lPGS = 2.15 i G4 = i G6 i 1PGS = 1.79
Prüfen der in den Ungleichungen (2) und (3) definierten erfindungsgemäßenChecking the inequalities defined in inequalities (2) and (3).
Kriterien beim beispielhaften Getriebedesign:
Figure imgf000015_0002
. . Criteria for the exemplary gearbox design:
Figure imgf000015_0002
. .
Prüfen der progressiven Getriebeabstufung des beispielhaften Getriebedesign anhand des in Ungleichung (5) definierten Kriteriums:
Figure imgf000016_0001
. . . . . Checking the progressive gear ratio of the exemplary gear design using the criterion defined in inequality (5):
Figure imgf000016_0001
. . . . .
Somit werden die Ungleichungen (2), (3) und (5) erfüllt. Thus, inequalities (2), (3) and (5) are satisfied.
Bei der in Fig. 3 dargestellten zweiten Ausführungsvariante sind die Getriebeebenen 85 und 86 der Zahnradpaare 3/5 und 4/6 im Vergleich zur ersten Ausführungsvariante vertauscht. In the second embodiment variant shown in FIG. 3, the gear levels 85 and 86 of the gear pairs 3/5 and 4/6 are swapped compared to the first embodiment variant.
Bei der in Fig. 4 dargestellten dritten Ausführungsvariante entspricht die Zahnradpaaranordnung 20 der zweiten Ausführungsvariante. Der Planetenradsatz PGS ist aber konzentrisch zur Primärantriebsmaschine ICE und zur Sekundärantriebsmaschine EM angeordnet, wobei die Achse Pa des Planetenradsatzes PGS bezüglich der Eingangswelle 14 versetzt, also parallel und mit Abstand zur Eingangswelle 14 ausgebildet ist. Der durch eine Zahnradstufe gebildete Primärtrieb PD verbindet das - hier als Planetenträger ausgebildete - dritte Glied P3 des Planetenradsatzes PGS mit der Eingangswelle 14 der schaltbaren Zahnradpaaranordnung 20 des Getriebes 13. Das erste Schaltelement CI blockiert den Planetenradsatz PGS in der - in Fig. 4 linken - ersten Schaltstellung L, indem es das - hier als Hohlrad ausgebildete - erste Glied PI mit dem - hier als Sonnenrad ausgebildeten - zweiten Glied P2 des Planetenradsatzes PGS verbindet. In the third embodiment variant shown in FIG. 4, the gear pair arrangement 20 corresponds to the second embodiment variant. However, the planetary gear set PGS is arranged concentrically to the primary drive machine ICE and to the secondary drive machine EM, the axis Pa of the planetary gear set PGS being offset with respect to the input shaft 14, i.e. parallel and at a distance from the input shaft 14. The primary drive PD, formed by a gear stage, connects the third link P3 of the planetary gear set PGS - here designed as a planet carrier - with the input shaft 14 of the switchable gear pair arrangement 20 of the transmission 13. The first switching element CI blocks the planetary gear set PGS in the - left in Fig. 4 - first switching position L by connecting the first link PI - here designed as a ring gear - with the second link P2 of the planetary gear set PGS - here designed as a sun gear.
Die Fig. 5, 6 und 7 zeigen Ausführungsvarianten von erfindungsgemäßen Antriebseinheiten 11, welche besonders für mehrspurige Kraftfahrzeuge - insbesondere Personenkraftwagen - geeignet sind. Bei Anwendung der Antriebseinheit 12 für ein mehrspuriges Kraftfahrzeug werden insbesondere eine Parksperrvorrichtung und ein Rückwärtsfahrfunktion vorgesehen. Diese Ausführungsvarianten sind insbesondere für Personenkraftfahrzeuge mit Vorderradantrieb vorteilhaft, wobei die Antriebseinheit 12 beispielsweise quer verbaut wird. Mit Bezugszeichen 30 ist bei jeder der beiden vierten, fünften und sechsten Ausführungsvarianten ein Differential bezeichnet, welches mit dem Finaltrieb FD des Getriebes 13 verbunden ist. Bei der in Fig. 5 gezeigten vierten Ausführungsvariante und bei der in Fig. 6 gezeigten sechsten Ausführungsvariante sind jeweils auf der ersten Zwischenwellen 16, bei der in Fig. 7 gezeigten sechsten Ausführungsvariante auf einer zweiten Zwischenwelle 160 ein Parksperrenrad P einer Parksperrvorrichtung sowie ein Losrad RL einer Rückwärtszahnradstufe RS angeordnet. Über die Rückwärtszahnradstufe RS lässt sich ein Rückwärtsgang GR mit Drehmomentfüllung während des Schaltvorganges realisieren. Die erste Zwischenwelle 16 ist über einen ersten Finaltrieb FD1 und die zweite Zwischenwelle 160 über einen zweiten Finaltrieb FD2 mit dem Differential 30 antriebsverbunden. 5, 6 and 7 show embodiment variants of drive units 11 according to the invention, which are particularly suitable for multi-lane motor vehicles - especially passenger cars. When using the drive unit 12 for a multi-lane motor vehicle, in particular a parking lock device and a reversing function are provided. These embodiment variants are particularly advantageous for passenger vehicles with front-wheel drive, with the drive unit 12 being installed transversely, for example. Reference numeral 30 denotes a differential in each of the two fourth, fifth and sixth embodiment variants, which is connected to the final drive FD of the transmission 13. In the fourth embodiment variant shown in FIG. 5 and in the sixth embodiment variant shown in FIG. 6, there is a parking lock wheel P on the first intermediate shaft 16, in the sixth embodiment variant shown in FIG a parking lock device and an idler gear RL of a reverse gear stage RS. A reverse gear GR with torque filling during the switching process can be achieved via the reverse gear stage RS. The first intermediate shaft 16 is drive-connected to the differential 30 via a first final drive FD1 and the second intermediate shaft 160 via a second final drive FD2.
Bei der vierten Ausführungsvariante ist die Sekundärantriebsmaschine EM als schnelllaufende Offset-Elektromaschine ausgebildet und mit dem beispielsweise als Sonnenrad ausgebildeten zweiten Glied P2 des Planetenradsatzes PGS über einen - beispielsweise als Stirnradgetriebe ausgeführten - Sekundärtrieb SD antriebsverbunden. In the fourth embodiment variant, the secondary drive machine EM is designed as a high-speed offset electric machine and is drive-connected to the second link P2 of the planetary gear set PGS, which is designed, for example, as a sun gear, via a secondary drive SD - designed, for example, as a spur gear.
Die Zahnradpaare 1/2, 3/5, 4/6 der Zahnradpaaranordnung 20 sind als Schrägverzahnung ausgeführt. Die Axialkräfte lassen eine Ausführung der Schaltelemente als Schieberäder nicht zu. Die Schaltelemente CI, C2, C3 sind daher als Schalthülsen ausgebildet. The gear pairs 1/2, 3/5, 4/6 of the gear pair arrangement 20 are designed as helical teeth. The axial forces do not allow the switching elements to be designed as sliding wheels. The switching elements CI, C2, C3 are therefore designed as switching sleeves.
Das erste Schaltelement CI arretiert den Planetenradsatz PGS in der - in den Fig. 5, 6, 7 linken - ersten Schaltstellung L , indem das als Hohlrad ausgebildete erste Glied PI mit dem als Sonnenrad ausgebildeten zweiten Glied P2 verbunden wird. In der - in den Fig. 5, 6 rechten - zweiten Schaltstellung R arretiert das erste Schaltelement CI die Primärantriebsmaschine ICE, indem es das erste Glied PI mit dem Gehäuse H verbindet. The first switching element CI locks the planetary gear set PGS in the first switching position L - on the left in FIGS. 5, 6, 7 - by connecting the first link PI, designed as a ring gear, to the second link P2, designed as a sun gear. In the second switching position R - on the right in FIGS. 5, 6 - the first switching element CI locks the primary drive machine ICE by connecting the first link PI to the housing H.
Dabei sind die zweiten C2 und dritten Schaltelemente C3 als Doppelschalthülsen ausgeführt, die im Raum zwischen den Losrädern 2L und 6L bzw. 5L und RL axial verschiebbar angeordnet sind. The second C2 and third switching elements C3 are designed as double switching sleeves, which are arranged axially displaceably in the space between the idler gears 2L and 6L or 5L and RL.
Mit Bezugszeichen 28 ist ein Reibungsmomentbegrenzer bezeichnet. Reference number 28 denotes a friction torque limiter.
Die Fig. 6 zeigt als fünfte Ausführungsvariante eine Variation der vierten Ausführungsvariante mit koaxial zum Planetenradsatz PGS und zur Primärantriebsmaschine ICE angeordneter Sekundärantriebsmaschine EM. 6 shows, as a fifth embodiment, a variation of the fourth embodiment with a secondary drive machine EM arranged coaxially to the planetary gear set PGS and to the primary drive machine ICE.
Das Getriebe 13 weist in der in Fig. 5 gezeigten vierten Ausführungsvariante und in der in Fig. 6 gezeigten fünften Ausführungsvariante folgendes Schaltschema auf: Stationäre Modi:
Figure imgf000018_0001
The transmission 13 has the following switching pattern in the fourth embodiment variant shown in FIG. 5 and in the fifth embodiment variant shown in FIG. 6: Stationary modes:
Figure imgf000018_0001
Transiente Modi:
Figure imgf000018_0002
Figure imgf000019_0001
Transient modes:
Figure imgf000018_0002
Figure imgf000019_0001
In der Schalttabelle bedeuten Meaning in the switching table
L Schaltung nach links (bezogen auf Fig. 5 oder Fig. 6) L Shift to the left (related to Fig. 5 or Fig. 6)
R Schaltung nach rechts (bezogen auf Fig. 5 oder Fig. 6) R switching to the right (related to Fig. 5 or Fig. 6)
X aktiviert X activated
NO neutraler Gang NO neutral gear
SC Laden der Fahrzeugbatterie SC Charging the vehicle battery
El erster Gang im EV-Modus El first gear in EV mode
E2 zweiter Gang im EV-Modus E2 second gear in EV mode
Gl erster Gang im ICE- und Hybridmodus Gl first gear in ICE and hybrid mode
G2 zweiter Gang im ICE- und Hybridmodus G2 second gear in ICE and hybrid mode
G3 dritter Gang im ICE- und Hybridmodus G3 third gear in ICE and hybrid mode
G4 vierter Gang im ICE- und Hybridmodus G4 fourth gear in ICE and hybrid mode
G5 fünfter Gang im ICE- und Hybridmodus G5 fifth gear in ICE and hybrid mode
G6 sechster Gang im ICE- und Hybridmodus G6 sixth gear in ICE and hybrid mode
GR. Rückwärtsgang im ICE- und Hybridmodus GR. Reverse gear in ICE and hybrid mode
In Fig. 7 ist eine sechste Ausführungsvariante als weitere Variationen der vierten Ausführungsvariante dargestellt. Das Getriebe 13 weist eine erste Zwischenwelle 16 und eine zweite Zwischenwelle 160 auf. Das erste Schaltelement CI ist - unterschiedlich zur vierten Ausführungsvariante - im Bereich des dem Planetenradsatz PGS abgewandten Endes der Eingangswelle 14 angeordnet und somit auf die der Antriebsseite abgewandte Rückseite des Getriebes 13 verlagert. Die mit dem ersten Glied PI des Planetenradsatzes PGS drehfest verbundene Antriebswelle 15 der Primärantriebsmaschine ICE ist durch die mit dem dritten Glied P3 - dem Planetenträger - des Planetenradsatzes PGS drehfest verbundene hohle Eingangswelle 14 geführt. Das erste Schaltelement CI ist also auf die der Antriebsseite S1 abgewandte Rückseite S2 des Getriebes 13 verlagert und verbindet wahlweise in der - in Fig. 7 rechten - zweiten Schaltstellung R die innere Antriebswelle 15 mit der hohlen Eingangswelle 14 - und damit mit dem Planetenträger P3 (rechte Position) oder in der - in Fig. 7 linken - ersten Schaltstellung L die Antriebswelle 15 mit dem Gehäuse H. In Fig. 7 a sixth embodiment variant is shown as further variations of the fourth embodiment variant. The transmission 13 has a first intermediate shaft 16 and a second intermediate shaft 160. The first switching element CI is - unlike the fourth embodiment variant - arranged in the area of the end of the input shaft 14 facing away from the planetary gear set PGS and thus shifted to the rear of the transmission 13 facing away from the drive side. The drive shaft 15 of the primary drive machine ICE, which is non-rotatably connected to the first link PI of the planetary gear set PGS, is guided by the hollow input shaft 14 which is non-rotatably connected to the third link P3 - the planet carrier - of the planetary gear set PGS. The first switching element CI is therefore shifted to the rear side S2 of the transmission 13 facing away from the drive side S1 and optionally connects the inner drive shaft 15 with the hollow input shaft 14 - and thus with the planet carrier P3 (in the right-hand side in FIG. 7) second switching position R ( right position) or in the first switching position L - left in FIG. 7 - the drive shaft 15 with the housing H.
Die Sekundärantriebsmaschine EM ist auch hier als schnelllaufende Offset- Elektromaschine ausgebildet, die über einen beispielsweise als Stirnradstufe ausgebildeten Sekundärtrieb SD mit dem zweiten Glied P2 - dem Sonnenrad - des Planetenradsatzes PGS verbunden ist, wobei der Sekundärtrieb SD in der Nähe des Drehschwingungsdämpfers D angeordnet ist, wodurch die Offset-Elektromaschine mit einer größtmöglichen axialen Erstreckung ausgeführt werden kann. The secondary drive machine EM is also designed here as a high-speed offset electric machine, which is connected to the second link P2 - the sun gear - of the planetary gear set PGS via a secondary drive SD designed, for example, as a spur gear stage, the secondary drive SD being arranged in the vicinity of the torsional vibration damper D, whereby the offset electric machine can be designed with the greatest possible axial extension.
Im Bereich der Rückseite S2 des Getriebes 13 ist auf der zweiten Zwischenwelle 160 das Parksperrenrad P einer Parksperrvorrichtung angeordnet. Das Parksperrenrad P liegt hier in derselben Ebene EP wie das erste Schaltelement CI. In the area of the rear side S2 of the transmission 13, the parking lock wheel P of a parking lock device is arranged on the second intermediate shaft 160. The parking lock wheel P lies here in the same plane EP as the first switching element CI.
Das Losrad RL der Rückwärtszahnradstufe RS ist auf der zweiten Zwischenwelle 160 angeordnet und kämmt mit dem Losrad 2L des Zahnradpaares 1/2. The idler gear RL of the reverse gear stage RS is arranged on the second intermediate shaft 160 and meshes with the idler gear 2L of the gear pair 1/2.
Das auf der zweiten Zwischenwelle 160 drehbar angeordnete Losrad 5L des Zahnradpaares 3/5 und das auf der ersten Zwischenwelle 16 drehbar angeordnete Losrad 6L des Zahnradpaares 4/6 sind mit einem gemeinsamen Festrad 5F, 6F auf der Eingangswelle 14 im Eingriff. Dabei sind die beiden Losräder 5L und RL wahlweise über das zweite Schaltelement C2 aktivierbar oder deaktivierbar. In der einer Mittelstellung entsprechenden Neutralstellung N des zweiten Schaltelementes C2 sind beide Losräder 5L und RL deaktiviert, also von der zweiten Zwischenwelle 160 getrennt. The idler gear 5L of the gear pair 3/5, which is rotatably arranged on the second intermediate shaft 160, and the idler gear 6L of the gear pair 4/6, which is rotatably arranged on the first intermediate shaft 16, are in engagement with a common fixed gear 5F, 6F on the input shaft 14. The two idler gears 5L and RL can either be activated or deactivated via the second switching element C2. In the neutral position N of the second switching element C2, which corresponds to a middle position, both idler gears 5L and RL are deactivated, i.e. separated from the second intermediate shaft 160.
Die Antriebseinheit 12 in der sechsten Ausführungsvariante weist - im Vergleich zur vierten Ausführungsvariante - ein viel kürzere axiale Erstreckung und eine reduzierte Anzahl an Zahnrädern auf. The drive unit 12 in the sixth embodiment variant has - compared to the fourth embodiment variant - a much shorter axial extension and a reduced number of gears.
Alle Ausführungsvarianten der Erfindung weisen folgende Eigenschaften auf: • Sechs Gänge Gl bis G6 mit progressiver Gangabstufung über nur 3 Zahneingriffe All embodiment variants of the invention have the following properties: • Six gears Gl to G6 with progressive gear gradation over only 3 tooth meshes
• Keine Reibungskupplungen und Synchronisierungen • No friction clutches and synchronizers
• Kurze Bauweise • Short design
• Geringe Anzahl von Komponenten • Low number of components
• Geringes Gewicht • Low weight
• Die Gänge G5 und G6 bilden Reiseübersetzungen mit hohem Wirkungsgrad aus. Dabei ist keine Drehmomentstützung der Sekundärantriebsmaschine EM wie bei den Gängen Gl, G3 und G4 erforderlich. • Gears G5 and G6 provide high-efficiency travel gear ratios. No torque support from the secondary drive machine EM is required, as is the case with gears Gl, G3 and G4.
• Bei dem kritischen Gangwechsel G1-G2 erfolgt mittels der Sekundärantriebsmaschine EM eine Drehmomentauffüllung; • During the critical gear change G1-G2, torque is replenished using the secondary drive machine EM;
• Es lässt sich ein energieeffizienter Start der Primärantriebsmaschine ICE auch bei niedrigem Batterie-Ladezustand durchführen. Dabei wird die Sekundärantriebsmaschine EM im Generatormodus betrieben; • An energy-efficient start of the ICE primary drive engine can be carried out even when the battery charge level is low. The secondary drive machine EM is operated in generator mode;
• Es ist ein Kaltstart der Primärantriebsmaschine ICE mit hohem Drehmoment (im Stillstand) möglich; • A cold start of the ICE primary drive machine with high torque (at standstill) is possible;
• Es ist ein Warmstart der Primärantriebsmaschine ICE während der Fahrt (Umschalten von Elektro- auf Hybridbetrieb) möglich; • It is possible to warm start the ICE primary drive engine while driving (switching from electric to hybrid operation);
• 48 V Mildhybrid ist möglich. Die Sekundärantriebsmaschine EM mit einer Leistung von 10..15% der ICE-Leistung ermöglicht den vollen Funktionsumfang (Kalt-/Warmschleppen, Start der Primärantriebsmaschine ICE, Boost/Regeneratives Bremsen, EV-Fahren im Stau); • 48 V mild hybrid is possible. The secondary drive machine EM with an output of 10..15% of the ICE power enables the full range of functions (cold/warm towing, starting the primary drive machine ICE, boost/regenerative braking, EV driving in traffic jams);
Bei der vorliegenden Erfindung ist in jeder dargestellten Ausführungsvariante die Primärantriebsmaschine ICE mit dem Hohlrad des Planetenradsatzes PGS verbunden, so dass der Schaltvorgang G1-G2 mit aktiver Drehmomentauffüllung ATF erfolgen kann (positives Drehmoment der Sekundärantriebsmaschine EM, positive Drehzahl der Sekundärantriebsmaschine EM während des Schaltvorgangs, Batterie wird geladen und/oder elektrische Energie wird abgeführt). In the present invention, in each embodiment variant shown, the primary drive machine ICE is connected to the ring gear of the planetary gear set PGS, so that the switching process G1-G2 can take place with active torque filling ATF (positive torque of the secondary drive machine EM, positive speed of the secondary drive machine EM during the switching process, battery is charged and/or electrical energy is dissipated).

Claims

P A T E N T A N S P R Ü C H E Antriebseinheit (12) für ein Kraftfahrzeug, insbesondere für ein Motorrad (11), mit einer Primärantriebsmaschine (ICE), einer Sekundärantriebsmaschine (EM) und einem Getriebe (13), welche Antriebseinheit (12) aufweist: P A T E N T A N P R U C H E Drive unit (12) for a motor vehicle, in particular for a motorcycle (11), with a primary drive machine (ICE), a secondary drive machine (EM) and a transmission (13), which drive unit (12) has:
• eine Eingangswelle (14); • an input shaft (14);
• eine Ausgangswelle (17); • an output shaft (17);
• einer ersten Zwischenwelle (16), die parallel zu der Eingangswelle (14) angeordnet und mit der Ausgangswelle (17) verbunden ist; • a first intermediate shaft (16) arranged parallel to the input shaft (14) and connected to the output shaft (17);
• einen Planetenradsatz (PGS) mit einem ersten (PI), zweiten (P2) und dritten Glied (P3), wobei das erste Glied (PI) mit der Primärantriebsmaschine (ICE), das zweite Glied (P2) mit der Sekundärantriebsmaschine (EM) und das dritte Glied (P3) mit der Eingangswelle (14) verbunden sind; • a planetary gear set (PGS) with a first (PI), second (P2) and third link (P3), the first link (PI) with the primary drive machine (ICE), the second link (P2) with the secondary drive machine (EM) and the third member (P3) is connected to the input shaft (14);
• zumindest ein erstes Schaltelement (CI), welches ausgebildet ist, um in einer Schaltstellung zwei Glieder (Pl, P3) des Planetenradsatzes (PGS) miteinander drehfest zu verbinden und in einer weiteren Schaltstellung die Primärantriebsmaschine (ICE) mit einem Gehäuse (H) des Getriebes (13) zu verbinden und zu blockieren; • at least one first switching element (CI), which is designed to connect two members (Pl, P3) of the planetary gear set (PGS) to one another in a rotationally fixed manner in a switching position and to connect the primary drive machine (ICE) to a housing (H) of the in a further switching position to connect and block the gear (13);
• einer Zahnradpaaranordnung (20) mit mehreren Zahnradpaaren (1/2, 3/5, 4/6) wobei jedes Zahnradpaar (20) ein Festrad (2F, 5F, 6F) und ein Losrad (2L, 5L, 6L) aufweist, wobei jedes Losrad (2L, 5L, 6L) über ein Schaltelement (C2, C3) aktivier- oder deaktivierbar ist, wobei • a gear pair arrangement (20) with several gear pairs (1/2, 3/5, 4/6), each gear pair (20) having a fixed gear (2F, 5F, 6F) and an idler gear (2L, 5L, 6L), where each idler gear (2L, 5L, 6L) can be activated or deactivated via a switching element (C2, C3), whereby
• die Zahnradpaare (1/2, 3/5, 4/6) die Übersetzungsverhältnisse IG2, ics, ice aufweisen, und wobei • the gear pairs (1/2, 3/5, 4/6) have the gear ratios IG2, ics, ice, and where
• die Losräder (2L, 5L, 6L) von zumindest zwei Zahnradpaaren (1/2, 3/5, 4/6) auf der ersten Zwischenwelle (16) drehbar gelagert sind, und die Festräder (2F, 5F, 6F) von diesen zumindest zwei Zahnradpaaren (1/2, 3/5, 4/6) auf der Eingangswelle (14) drehfest angeordnet sind; dadurch gekennzeichnet, dass gilt: ilPGS> 1, wobei iiPGs ein Übersetzungsverhältnis des Planetenradsatzes (PGS) von dem ersten Glied (PI) zur Eingangswelle (14) mit angehaltener Sekundärantriebsmaschine (EM) ist, und dass • the loose gears (2L, 5L, 6L) of at least two gear pairs (1/2, 3/5, 4/6) are rotatably mounted on the first intermediate shaft (16), and the fixed gears (2F, 5F, 6F) of these at least two pairs of gears (1/2, 3/5, 4/6) are arranged on the input shaft (14) in a rotationally fixed manner; characterized in that: ilPGS> 1, where iiPGs is a gear ratio of the planetary gear set (PGS) from the first link (PI) to the input shaft (14) with the secondary drive machine (EM) stopped, and that
• die Übersetzungsverhältnisse IG2, ics, iG6, iiPGs mindestens eine der folgenden Ungleichungen erfüllen:
Figure imgf000023_0001
Antriebseinheit (12) nach einem der Ansprüche 1 bis 3, dadu rch geken nzeichnet, dass das Getriebe (13) eine progressive Gangabstufung aufweist, wobei für die Übersetzungen iGi, iG2, ics, iG4, ics, ie gilt:
Figure imgf000023_0002
Antriebseinheit (12) nach einem der Ansprüche 1 bis 4, dadu rch geken nzeichnet, dass für die Übersetzungen iiPGs, IGI, iG2 gilt:
Figure imgf000023_0003
Antriebseinheit (12) nach einem der Ansprüche 1 bis 5, dadurch geken nzeichnet, dass das erste Glied (PI) des Planetenradsatzes (PGS) als Hohlrad, das zweite Glied (P2) des Planetenradsatzes (PGS) als Sonnenrad und das dritte Glied (P3) des Planetenradsatzes (PGS) als Planetenträger ausgebildet ist. Antriebseinheit (12) nach Anspruch 6, dadurch gekennzeichnet, dass gilt
Figure imgf000023_0004
wobei zi die Anzahl der Zähne des Sonnenrades und Z2 die Anzahl der Zähne des Hohlrades ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 5, dadurch geken nzeichnet, dass das Losrad (2L, 5L, 6L) eines Zahnradpaares (1/2, 3/5, 4/6) auf der Eingangswelle (14) drehbar gelagert ist, und das Festrad (2 F, 5F, 6F) dieses Zahnradpaares (1/2, 3/5, 4/6) auf der Zwischenwelle (16) drehfest angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 5, dadurch geken nzeichnet, dass das Losrad (6L) eines Zahnradpaares (4/6) auf der ersten Zwischenwelle (16) und das Losrad (5L) eines anderen Zahnradpaares (3/5) auf einer zweiten Zwischenwelle (160) drehbar gelagert ist, wobei die beiden Losräder (6L, 5L) mit einem gemeinsamen Festrad (5F, 6F) auf der Eingangswelle (14) im Zahneingriff stehen. Antriebseinheit (12) nach einem der Ansprüche 1 bis 5, dadurch geken nzeichnet, dass die Losräder (2L, 5L, 6L) von zumindest drei Zahnradpaaren (1/2, 3/5, 4/6) auf der ersten Zwischenwelle (16) drehbar gelagert sind, und die Festräder (2F, 5F, 6F) von diesen zumindest drei Zahnradpaare (1/2, 3/5, 4/6) auf der Eingangswelle (14) drehfest angeordnet sind. Antriebseinheit (12) nach einem der Ansprüche 1 bis 5, dadurch geken nzeichnet, dass die Antriebseinheit (12) zumindest eine Rückwärtsgangzahnradstufe (RS) aufweist, wobei ein Losrad (RL) der Rückwärtsgangzahnradstufe (RS) auf der ersten Zwischenwelle (16) oder der zweiten Zwischenwelle (160) drehbar gelagert ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 6, dadurch geken nzeichnet, dass der Planetenradsatz (PGS) zwischen der Zahnradpaaranordnung (20) und der Sekundärantriebsmaschine (EM) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 6 oder 10, dadurch geken nzeichnet, dass die Sekundärantriebsmaschine (EM) koaxial mit dem Planetenradsatz (PGM) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 6, 10 oder 11, dadurch geken nzeichnet, dass die Primärantriebsmaschine (ICE) koaxial mit dem Planetenradsatz (PGS) und der Sekundärantriebsmaschine (EM) und distanziert zur Eingangswelle (14) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 5 oder 7 bis 9, dadurch geken nzeichnet, dass die Primärantriebsmaschine (ICE) koaxial mit dem Planetenradsatz (PGS) und die Sekundärantriebsmaschine (EM) parallel und distanziert zur Eingangswelle (14) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 6 oder 8 bis 11, dadurch gekennzeichnet, dass die Primärantriebsmaschine (ICE) koaxial mit der Sekundärantriebsmaschine (EM) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 14, dadu rch geken nzeichnet, dass die Antriebseinheit (12) eine Parksperrvorrichtung mit zumindest einem sperrbaren Parksperrenrad (P) aufweist, wobei das Parksperrenrad (P) auf der ersten Zwischenwelle (16) oder der zweiten Zwischenwelle (160) angeordnet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 15, dadurch geken nzeichnet, dass zumindest ein Schaltelement (CI, C2, C3) durch eine axial verschiebbare Schalthülse - vorzugsweise eine Doppelschalthülse - gebildet ist Antriebseinheit (12) nach einem der Ansprüche 1 bis 16, dadurch geken nzeichnet, dass zumindest ein Schaltelement (C2, C3) einstückig mit einem Festrad (5F, 6F) zumindest eines benachbarten Zahnradpaares (3/5, 4/6) ausgebildet ist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 17, dadurch geken nzeichnet, dass zumindest ein Schaltelement (CI, C2, C3) zwei Schaltstellungen (L, R) und vorzugsweise zwischen einer ersten (L) und einer zweiten Schaltstellung (R) eine Neutralstellung (N) aufweist. Antriebseinheit (12) nach einem der Ansprüche 1 bis 18, dadurch geken nzeichnet, dass die Primärantriebsmaschine (ICE) eine Brennkraftmaschine und die Sekundärantriebsmaschine (EM) eine elektrische Maschine ist. Kraftfahrzeug, insbesondere Motorrad (11) , mit einer Antriebseinheit (12) nach einem der Ansprüche 1 bis 19, dadurch geken nzeichnet, dass das Getriebe (13) ausgebildet ist, um zumindest einen Gangwechsel - vorzugsweise vom ersten Gang (Gl) in den zweiten Gang (G2) - mit aktiver Drehmomentauffüllung durch die Sekundärantriebsmaschine (EM) durchzuführen. • the gear ratios IG2, ics, iG6, iiPGs satisfy at least one of the following inequalities:
Figure imgf000023_0001
Drive unit (12) according to one of claims 1 to 3, characterized in that the transmission (13) has a progressive gear gradation, the following applies to the translations i G i, iG2, ics, iG4, ics, ie:
Figure imgf000023_0002
Drive unit (12) according to one of claims 1 to 4, characterized in that the following applies to the translations ii PG s, IGI, iG2:
Figure imgf000023_0003
Drive unit (12) according to one of claims 1 to 5, characterized in that the first link (PI) of the planetary gear set (PGS) is designed as a ring gear, the second link (P2) of the planetary gear set (PGS) is designed as a sun gear and the third link (P3 ) of the planetary gear set (PGS) is designed as a planet carrier. Drive unit (12) according to claim 6, characterized in that applies
Figure imgf000023_0004
where zi is the number of teeth of the sun gear and Z2 is the number of teeth of the ring gear. Drive unit (12) according to one of claims 1 to 5, characterized in that the idler gear (2L, 5L, 6L) of a pair of gears (1/2, 3/5, 4/6) is rotatably mounted on the input shaft (14). , and the fixed gear (2 F, 5F, 6F) of this pair of gears (1/2, 3/5, 4/6) is arranged in a rotationally fixed manner on the intermediate shaft (16). Drive unit (12) according to one of claims 1 to 5, characterized in that the idler gear (6L) of a pair of gears (4/6) on the first intermediate shaft (16) and the idler gear (5L) of another pair of gears (3/5) is rotatably mounted on a second intermediate shaft (160), the two idler gears (6L, 5L) meshing with a common fixed gear (5F, 6F) on the input shaft (14). Drive unit (12) according to one of claims 1 to 5, characterized in that the idler gears (2L, 5L, 6L) of at least three gear pairs (1/2, 3/5, 4/6) on the first intermediate shaft (16) are rotatably mounted, and the fixed gears (2F, 5F, 6F) of these at least three pairs of gears (1/2, 3/5, 4/6) are arranged in a rotationally fixed manner on the input shaft (14). Drive unit (12) according to one of claims 1 to 5, characterized in that the drive unit (12) has at least one reverse gear stage (RS), an idler gear (RL) of the reverse gear stage (RS) being on the first intermediate shaft (16) or the second intermediate shaft (160) is rotatably mounted. Drive unit (12) according to one of claims 1 to 6, characterized in that the planetary gear set (PGS) is arranged between the gear pair arrangement (20) and the secondary drive machine (EM). Drive unit (12) according to one of claims 1 to 6 or 10, characterized in that the secondary drive machine (EM) is arranged coaxially with the planetary gear set (PGM). Drive unit (12) according to one of claims 1 to 6, 10 or 11, characterized in that the primary drive machine (ICE) is arranged coaxially with the planetary gear set (PGS) and the secondary drive machine (EM) and at a distance from the input shaft (14). Drive unit (12) according to one of claims 1 to 5 or 7 to 9, characterized in that the primary drive machine (ICE) is arranged coaxially with the planetary gear set (PGS) and the secondary drive machine (EM) is arranged parallel and at a distance from the input shaft (14). Drive unit (12) according to one of claims 1 to 6 or 8 to 11, characterized in that the primary drive machine (ICE) is arranged coaxially with the secondary drive machine (EM). Drive unit (12) according to one of claims 1 to 14, characterized in that the drive unit (12) has a parking lock device with at least one lockable parking lock wheel (P), the parking lock wheel (P) being on the first intermediate shaft (16) or the second intermediate shaft (160) is arranged. Drive unit (12) according to one of claims 1 to 15, characterized in that at least one switching element (CI, C2, C3) is formed by an axially displaceable switching sleeve - preferably a double switching sleeve. Drive unit (12) according to one of claims 1 to 16 , characterized in that at least one switching element (C2, C3) is formed in one piece with a fixed gear (5F, 6F) of at least one adjacent gear pair (3/5, 4/6). Drive unit (12) according to one of claims 1 to 17, characterized in that at least one switching element (CI, C2, C3) has two switching positions (L, R) and preferably between a first (L) and a second switching position (R). Has neutral position (N). Drive unit (12) according to one of claims 1 to 18, characterized in that the primary drive machine (ICE) is an internal combustion engine and the secondary drive machine (EM) is an electric machine. Motor vehicle, in particular motorcycle (11), with a drive unit (12) according to one of claims 1 to 19, characterized in that the Transmission (13) is designed to carry out at least one gear change - preferably from first gear (Gl) to second gear (G2) - with active torque filling by the secondary drive machine (EM).
PCT/AT2023/060272 2022-08-09 2023-08-09 Drive unit for a motor vehicle WO2024031122A1 (en)

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US10569635B2 (en) * 2018-01-25 2020-02-25 Zhihui Duan Hybrid electric drive train of a motor vehicle
AT524454B1 (en) * 2020-11-26 2022-08-15 Avl List Gmbh DRIVE TRAIN FOR A MOTOR VEHICLE

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0845618A2 (en) 1996-11-30 1998-06-03 Volkswagen Aktiengesellschaft Contiuously-variable multi-speed transmission
WO2000020243A1 (en) 1998-10-02 2000-04-13 Luk Lamellen Und Kupplungsbau Gmbh Transmission comprising at least two shafts and an electric motor or an automated clutch
WO2001007278A1 (en) * 1999-07-23 2001-02-01 Zf Friedrichshafen Ag Electrodynamic drive train
DE102005040153A1 (en) * 2005-08-25 2007-03-01 Zf Friedrichshafen Ag Gearing system for e.g. lorry, has electrodynamic driving unit arranged between combustion engine and control gear, and reverse gear realized by corresponding alignment of electric motor such that vehicle is driven by electric motor
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DE102020007777A1 (en) * 2020-12-18 2022-06-23 Mercedes-Benz Group AG hybrid drive system

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