WO2020002013A1 - Système de propulsion hybride - Google Patents

Système de propulsion hybride Download PDF

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Publication number
WO2020002013A1
WO2020002013A1 PCT/EP2019/065814 EP2019065814W WO2020002013A1 WO 2020002013 A1 WO2020002013 A1 WO 2020002013A1 EP 2019065814 W EP2019065814 W EP 2019065814W WO 2020002013 A1 WO2020002013 A1 WO 2020002013A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
spur gear
countershaft
input shaft
combustion engine
Prior art date
Application number
PCT/EP2019/065814
Other languages
German (de)
English (en)
Inventor
Tobias Schilder
Klaus Riedl
Tobias Haerter
Original Assignee
Daimler Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Ag filed Critical Daimler Ag
Priority to CN201980042997.8A priority Critical patent/CN112384398A/zh
Publication of WO2020002013A1 publication Critical patent/WO2020002013A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—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
    • B60K6/22—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
    • 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
    • B60K6/22—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
    • B60K6/40—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 assembly or relative disposition of components
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the invention relates to a hybrid drive system and a motor vehicle with a
  • Hybrid drive systems are already known, for example from DE 10 2010 063 580 A1 and DE 10 2013 211 975 A1.
  • a hybrid drive system is already known from the generic DE 10 2013 221 461 A1, in which both a first unit consisting of a
  • the invention is particularly based on the object of providing an advantageously compact hybrid drive system. It is an inventive
  • the invention is based on a hybrid drive system with an internal combustion engine that has a crankshaft, with an electric drive unit that has an electric machine with a rotor and a stator, with a spur gear that has a first input shaft, a first countershaft, and an output, in particular an output spur gear pair, with a planetary gear, which has a second input shaft and an output shaft, and with an axle gear, wherein the crankshaft of the internal combustion engine is rotatably coupled to the first input shaft.
  • the electric drive unit is a
  • Has spur gear pair via which the rotor of the electrical machine can be coupled to the second input shaft of the planetary gear, the spur gear in a torque flow emanating from the internal combustion engine and directed to the axle gear before the output, exactly two switchable spur gear pairs, namely a first switchable spur gear pair and one second switchable spur gear pairing.
  • the spur gear pair of the electric drive unit is preferably arranged in the torque flow behind the output of the spur gear.
  • the spur gear pair of the electric drive unit is preferably a direct torque flow of the
  • the electrical machine can preferably be coupled to the second input shaft of the planetary gear via one or more separate spur gear stages, or it acts on an output gear of the output of the spur gear.
  • the planetary gear is in particular formed by a multi-speed, load-shiftable, axially parallel EV gear.
  • the spur gear transmission is formed in particular by an axially parallel multi-speed internal combustion engine transmission which is not power-shiftable per se.
  • the combination of the planetary gear and the spur gear can in particular be used to provide a hybrid group transmission in which, during the changeover in the spur gear, which basically takes place with load interruption, the electrical machine takes over the driving task via the planetary gear and thus supports the shifting, thereby resulting in a power shift becomes.
  • an advantageously axially short hybrid drive system can thereby be provided.
  • an axial gain in installation space can be achieved. This in turn enables the hybrid drive system to be installed transversely.
  • a hybrid drive system with a power shiftable hybrid gear can be provided with little axial construction, wherein in particular a spur gear that is not power shiftable can be used. This results in the use of a power switchable electrical
  • the hybrid drive system is intended in particular for a motor vehicle.
  • the hybrid drive system preferably serves to drive a motor vehicle, if necessary by means of the internal combustion engine and / or the electrical machine.
  • the electrical machine is in particular as an electric motor and / or as a
  • the electrical machine advantageously has a stator.
  • the rotor is particularly advantageously arranged radially inside the stator.
  • the stator is preferably permanently connected to a housing in a rotationally fixed manner.
  • the housing is installed in a position-fixed and rotationally fixed manner in the motor vehicle in an assembled state.
  • An “input shaft” is to be understood in particular to mean a gear element which forms a gear input of the respectively assigned gear group.
  • the input shaft is preferably provided for providing an input speed of the respectively assigned transmission group.
  • the first is preferred
  • the second input shaft is particularly preferably structurally provided for the rotationally fixed connection to the output of the spur gear.
  • An “output” is to be understood in particular as a gear element that forms a gear output of the respectively assigned gear group.
  • An “output shaft” is to be understood in particular to mean a gear element which is at least structurally provided for the rotationally fixed connection of an axle drive.
  • non-rotatable connection of two elements means that the two elements are arranged coaxially to one another and are connected to one another in such a way that they rotate at the same angular velocity.
  • a “planetary gear” is to be understood in particular as a gear that has at least one planet gear connected to a planet carrier, which is coupled in the radial direction outward with a ring gear and in the radial direction inward with a sun gear.
  • the planetary gear preferably has at least one planetary gear set, in particular a plurality of planetary gear sets.
  • a “planetary gear set” is to be understood in particular to mean a unit with a sun gear, a ring gear and with at least one planet gear guided by a planet gear carrier on a circular path around the sun gear.
  • Planet carrier and ring gears are referred to as elements of the planetary gear.
  • the planetary gear set advantageously has exactly one
  • a “spur gear pairing” is to be understood in particular to mean a pairing of at least two meshing gear wheels, in particular spur gear wheels, which are preferably arranged in a gear wheel plane.
  • the spur gear pair advantageously has exactly one gear ratio.
  • a “switchable spur gear pair” is to be understood in this context in particular as a switchable and / or uncouplable spur gear pair. This should preferably be understood to mean, in particular, a spur gear pair coupled to a switching unit, at least one spur gear, in particular an idler gear, of the spur gear pair being coupled to the switching unit.
  • the switchable spur gear pair preferably comprises at least one idler gear and at least one fixed gear.
  • switching unit in particular a unit with exactly two
  • Coupling elements are understood, which is provided to two rotatably mounted gear elements, such as an idler gear and one
  • Two adjacent, in particular axially adjacent, switching units can basically form a common double switching unit
  • each of the switching units can be in the form of a purely positive-locking switching unit, for example a claw clutch, a positive and frictional switching unit, for example in the form of a synchronized one
  • Claw clutch or as a purely frictional switching unit, for example in the form of a multi-plate clutch.
  • Spur gear pairs are arranged such that a torque of
  • Planetary gear is arranged coaxially to the side shafts of the axle drive. Overall, this makes it possible to create a compact hybrid drive system.
  • first input shaft of the spur gear is arranged coaxially with the crankshaft of the internal combustion engine.
  • the first input shaft is preferably connected to the crankshaft of the engine via at least one torsion damper
  • the first input shaft is connected to the crankshaft of the internal combustion engine via a clutch.
  • a clutch In this way, in particular an advantageously compact connection of the spur gear to the internal combustion engine can be achieved.
  • crankshaft of the internal combustion engine, the rotor of the electrical machine and the second input shaft of the planetary gear are arranged axially parallel and offset from one another.
  • the crankshaft of the internal combustion engine, the rotor of the electrical machine and the second input shaft are preferably arranged axially at least partially offset from one another.
  • the rotor of the electrical machine and the second input shaft of the planetary gear are arranged axially offset from the crank angle of the internal combustion engine.
  • an advantageously compact arrangement of the gears can be achieved in particular.
  • the axes can be offset, which enables an axially short hybrid drive system.
  • axle transmission be coaxial with the second
  • Input shaft of the planetary gear is arranged. This means that side shafts of the axle drive are arranged coaxially to the second input shaft of the planetary gear.
  • the second input shaft of the planetary gear is preferably designed as a hollow shaft which radially surrounds at least one of the side shafts of the axle drive at least in sections.
  • the first planetary gear set is particularly preferably arranged radially surrounding and at least partially axially overlapping to the axle drive.
  • the first planetary gear set is advantageously arranged radially surrounding and at least partially axially overlapping to a differential cage of the axle drive.
  • an element, that is to say either a ring gear or a planet gear carrier or a sun gear, of the planetary gear is advantageously connected in a rotationally fixed manner to the differential cage of the axle drive.
  • the “axle transmission” is to be understood in particular to mean a transmission of a motor vehicle which is intended to transmit a force of a drive unit of the motor vehicle to the axle of the drive wheels of the motor vehicle.
  • the axle drive is preferably provided to transmit a force from the transmission to the shaft of the drive wheels of the motor vehicle.
  • the axle drive is preferably formed, for example, by a differential gear.
  • the axle gear is preferably arranged coaxially to the at least one planetary gear set of the planetary gear, with the at least one planetary gear set being particularly preferably arranged to radially surround and axially overlap the axle gear. The overall result is a compact and at the same time efficient hybrid drive system.
  • the hybrid drive system have at least one
  • Separating clutch which is provided for a rotationally fixed coupling of the crankshaft of the internal combustion engine to the first input shaft of the spur gear, the separating clutch being arranged coaxially to the crankshaft of the internal combustion engine and the spur gear being arranged axially between the internal combustion engine and the separating clutch.
  • the separating clutch is preferably arranged on a side of the spur gear transmission facing away from the internal combustion engine. In this way, in particular, an advantageously arranged disconnect clutch can be provided. In particular, an advantageously close arrangement of the spur gear on the
  • the hybrid drive system can be equipped with and without an additional disconnect clutch. If it is not possible to start using the EM, the separating clutch can be dimensioned as a starting clutch. It can also be used in e-travel
  • the hybrid drive system preferably has at least one interposed torsional damper between the internal combustion engine and the spur gear.
  • Spur gear has a first countershaft gear, which is arranged coaxially to the first countershaft of the spur gear, and the second switchable
  • Spur gear pairing of the spur gear has a second countershaft gear, which is arranged coaxially to a second countershaft of the spur gear, the first countershaft, the second countershaft and the crankshaft being arranged axially parallel to one another.
  • the first countershaft gear of the first switchable spur gear pair is preferably formed by an idler gear. In principle, however, training as a fixed wheel would also be conceivable.
  • the second countershaft gear of the second switchable spur gear pair is preferably formed by an idler gear. In principle, however, training as a fixed wheel would also be conceivable. In this way, an advantageously compact, in particular axially compact, hybrid drive system can be achieved. This advantageously enables transverse installation of the hybrid drive system.
  • first switchable spur gear pair of the spur gear and the second switchable spur gear pair of the spur gear are arranged in a gear plane and an output gear of the first countershaft and an output gear of the second countershaft in a gear plane with the
  • Spur gear pairing of the electric drive unit are arranged.
  • the output gear of the second countershaft preferably forms a spur gear of the spur gear pair of the electric drive unit.
  • the electrical drive unit is preferably connected directly to the driven gear of the second countershaft.
  • Spur gear has a first countershaft gear, which is arranged coaxially to the first countershaft of the spur gear, and the second switchable
  • Spur gear pairing of the spur gear has a second countershaft gear, which is arranged coaxially to the first countershaft of the spur gear.
  • the first countershaft gear of the first switchable spur gear pair is preferably formed by a fixed gear. In principle, however, training as a loose wheel would also be conceivable.
  • the second countershaft gear of the second switchable spur gear pair is preferably formed by a fixed gear. In principle, however, training as a loose wheel would also be conceivable.
  • the first countershaft wheel and the second countershaft wheel are particularly preferably connected in a rotationally fixed manner to the first countershaft in at least one operating state, in particular permanently. In particular, the first countershaft gear and the second countershaft gear form fixed gears of the first
  • Spur gear has a first switching element, and the second switchable
  • Spur gear pairing of the spur gear has a second switching element, the first switching element and the second switching element being arranged coaxially with the first input shaft.
  • the first switching element and the second are preferred
  • the first switching element preferably forms part of a first switching unit and the second switching element forms part of a second switching unit.
  • the first switching element and the second switching element are preferably each formed by a claw switching element.
  • the claw switching elements can in particular with or without
  • the position of the switching elements of the spur gear can be anywhere between the crankshaft and the second input shaft of the planetary gear.
  • the countershaft of the spur gear can be divided into two countershafts.
  • the invention is based on a motor vehicle with the hybrid drive system.
  • a position of the spur gear pairings of the spur gear can fundamentally also differ from an arrangement described and shown.
  • gear levels of the same spur gear may also be exchanged for design reasons.
  • the first countershaft and the second countershaft may also be interchanged.
  • an arrangement of the electrical machine can also be changed.
  • the terms “axial” and “radial” here refer in particular to a main axis of rotation of the transmission, in particular the input shafts, so that the term “axial” denotes in particular a direction that is parallel or coaxial to the
  • Main axis of rotation runs. Furthermore, the term “radial” denotes in particular a direction that runs perpendicular to the main axis of rotation. Under one
  • “Gearbox input side arrangement” should be understood in particular to mean that the named component is arranged on one side of the further component which
  • Transmission input element and / or the internal combustion engine is facing.
  • a “transmission output side arrangement” is to be understood in particular to mean that the named component is arranged on a side of the further component which faces away from the transmission input element and / or the internal combustion engine, even if the further component is arranged in the axial direction after the transmission output element.
  • FIG. 1 is a schematic representation of a hybrid drive system according to the invention, with an internal combustion engine, with an electric drive unit, with a spur gear, with a planetary gear and with an axle gear,
  • Fig. 2 shows an alternative hybrid drive system according to the invention, with a
  • Fig. 3 shows another alternative hybrid drive system according to the invention, with a
  • FIG. 4 shows a further alternative hybrid drive system according to the invention, with an internal combustion engine, with an electric drive unit, with a spur gear, with a planetary gear and with an axle gear in a schematic representation.
  • FIG. 1 schematically shows a hybrid drive system 10a for a motor vehicle.
  • the motor vehicle is, for example, a car.
  • the motor vehicle is formed by a front-wheel drive motor vehicle.
  • the motor vehicle is formed by a front-wheel drive hybrid motor vehicle.
  • the motor vehicle comprises a drive train, via which drive wheels of the motor vehicle are no longer visible.
  • the drive train includes the hybrid drive system 10a.
  • the motor vehicle has the hybrid drive system 10a.
  • the hybrid drive system 10a has one
  • the internal combustion engine 1 1 a is in particular installed transversely.
  • the internal combustion engine 1 1a has a crankshaft 12a.
  • the crankshaft 12a extends in particular transversely to a straight-ahead direction.
  • Hybrid drive system 10a is installed transversely.
  • the hybrid drive system 10a has a front-transverse architecture.
  • the hybrid drive system 10a is transverse to one
  • the hybrid drive system 10a also has an electric drive unit 13a.
  • the electric drive unit 13a has an electric machine 14a which has a rotor 15a.
  • the electrical machine 14a has a stator 16a.
  • the electric machine 14a is arranged on a side of the hybrid drive system 10a facing away from the internal combustion engine 1 1a.
  • the electric machine 14a is provided in addition to the internal combustion engine 1 1a for generating a further drive torque.
  • the electric machine 14a forms an electric motor. It would also be possible to replace the electrical machine 14a with a hydraulic or pneumatic drive unit with a correspondingly assigned one
  • the electrical machine 14a is provided for selectively converting electrical energy into mechanical energy or converting mechanical energy into electrical energy.
  • the electrical machine 14a has the stator 16a and the rotor 15a.
  • the stator 16a is fixedly connected to a body of the motor vehicle.
  • the rotor 15a is rotatably arranged with respect to the stator 16a.
  • the motor vehicle has a battery device, not shown.
  • Battery device is provided to supply electrical energy to drive the electrical Provide machine 14a and store electrical energy from the
  • Internal combustion engine 11 a is generated or fed from an external power grid.
  • the hybrid drive system 10a also has a multi-speed transmission.
  • Hybrid drive system 10a has a spur gear 17a. Furthermore, the
  • Hybrid drive system 10a a planetary gear 20a.
  • the spur gear 17a has a first input shaft 18a and a first countershaft 19a.
  • the crankshaft 12a of the internal combustion engine 1 1a can be coupled in a rotationally fixed manner to the first input shaft 18a.
  • the first input shaft 18a of the spur gear 17a is arranged coaxially with the crankshaft 12a of the internal combustion engine 1 1a.
  • the hybrid drive system 10a has a torsion damper 26a, which is arranged between the input shaft 18a and the crankshaft 12a and connects them. Furthermore, the hybrid drive system 10a has a separating clutch 24a, which is provided for a rotationally fixed coupling of the crankshaft 12a of the internal combustion engine 11a to the first input shaft 18a of the spur gear 17a.
  • the disconnect clutch 24a is coaxial with the crankshaft 12a of the
  • the first input shaft 18a is designed as a hollow shaft through which the crankshaft 12a is passed.
  • the spur gear 17a is formed by spur gear sets with two spur gears.
  • the spur gear 17a has exactly two switchable spur gear pairs V1 a, V2a, namely a first switchable spur gear pair V1 a and a second switchable one
  • Helical gear pairing V2a on.
  • the second switchable spur gear pair V2a is, for example, on a side of the first switchable that faces away from the internal combustion engine 11a
  • Spur gear pairing V1a arranged.
  • the first switchable spur gear pair V1a and the second switchable spur gear pair V2a have different gear ratios.
  • the first switchable spur gear pair V1a of the spur gear 17a has a first input shaft gear V1 1a, which is arranged coaxially with the first input shaft 18a of the spur gear 17a.
  • the first input shaft gear V1 1a is arranged on the first input shaft 18a.
  • the first input shaft gear V11a is formed by a first idler gear of the first input shaft 18a.
  • the first switchable spur gear pair V1a of the spur gear 17a has a first countershaft gear V12a, which is arranged coaxially with the first countershaft 19a of the spur gear 17a.
  • the first countershaft gear V12a is on the first countershaft 19a arranged.
  • the first countershaft gear V12a is formed by a fixed gear of the first countershaft 19a.
  • the first input shaft gear V11 a meshes directly with the first countershaft gear V12a.
  • the first switchable spur gear pairing V1a is arranged in a first gear plane Z1a.
  • the second switchable spur gear pair V2a of the spur gear 17a has a second input shaft gear V21a, which is arranged coaxially to the first input shaft 18a of the spur gear 17a.
  • the second input shaft gear V21a is arranged on the first input shaft 18a.
  • the second input shaft gear V21a is formed by a second idler gear of the first input shaft 18a.
  • the second switchable spur gear pair V2a of the spur gear 17a has a second countershaft gear V22a, which is arranged coaxially with the first countershaft 19a of the spur gear 17a.
  • the second countershaft gear V22a is arranged on the first countershaft 19a.
  • the second countershaft gear V22a is formed by a fixed gear of the first countershaft 19a.
  • the second input shaft gear V21a meshes directly with the second countershaft gear V22a.
  • the second spur gear pair V2a is arranged in a third gear plane Z3a.
  • the first switchable spur gear pairing V1a of the spur gear 17a has a first switching unit S1a with a first switching element S11a.
  • the first switching element S1 1a is provided for releasable coupling of the first input shaft gear V1 1a to the first input shaft 18a.
  • the first switching element S1 1a is one
  • the first switching element S1 1 a is one
  • the second switchable spur gear pair V2a of the spur gear 17a has a second switching unit S2a with a second switching element S21a.
  • the second switching element S21a is provided for releasable coupling of the second input shaft gear V21a to the first input shaft 18a.
  • the second switching element S21a is formed by a claw switching element.
  • the second switching element S21a is formed by a synchronized claw switching element.
  • the first switching element S11 a and the second switching element S21a are coupled to one another, so that only one of the two switching elements S11 a,
  • the first switching element S1 1 a and the second switching element S21 a are also arranged coaxially to the first input shaft 18a.
  • the spur gear 17a for example, exactly two gears can be shifted.
  • the number of speed ratios between the internal combustion engine 11 a and the electrical machine 14 a corresponds to the number of gears
  • the spur gear 17a has an output V3a.
  • the output V3a is formed by an output spur gear pair.
  • the output V3a has a first output gear V31a, which is arranged coaxially with the first countershaft 19a of the spur gear 17a.
  • the first driven gear V31a is arranged on the first countershaft 19a.
  • the first driven gear V31a is from a third fixed gear the first
  • the output V3a of the spur gear 17a has a first input shaft gear V33a, which is arranged coaxially with a second input shaft 21a of the planetary gear 20a.
  • the first input shaft V33a is arranged on the second input shaft 21a.
  • the first input shaft gear V33a is formed by a fixed gear of the second input shaft 21a.
  • the first driven gear V31a meshes directly with the first input shaft gear V33a.
  • the output V3a of the spur gear 17a is arranged in a second gear plane Z2a.
  • the exactly two switchable spur gear pairs V1a, V2a of the spur gear 17a are arranged in the torque flow before the output V3a.
  • the output V3a forms an output of the spur gear 17a for the two switchable spur gear pairs V1 a, V2a.
  • the electric drive unit 13a has a spur gear pair V4a.
  • the rotor 15a of the electrical machine 14a can be coupled to the second input shaft 21a of the planetary gear 20a via the spur gear pair V4a.
  • the spur gear pair V4a of the electric drive unit 13a has a first spur gear V41 a, which is rotatably connected to the rotor 15a of the electric machine 14a. Furthermore, the spur gear pair V4a of the electric drive unit 13a has a second one
  • Input shaft wheel V42a which is arranged coaxially to a second input shaft 21a of the planetary gear 20a.
  • the second input shaft gear V42a is arranged on the second input shaft 21a.
  • the second input shaft gear V42a is formed by a fixed gear of the second input shaft 21a.
  • the first spur gear V41a meshes directly with the second input shaft gear V42a.
  • the spur gear pair V4a of the electric drive unit 13a is arranged in a fourth gear plane Z4a.
  • the planetary gear 20a is arranged behind the output V3a in the torque flow.
  • the planetary gear 20a has the second input shaft 21a and an output shaft 22a.
  • the planetary gear 20a is provided for transmitting a torque of the internal combustion engine 11a transmitted via the spur gear 17a and / or from the electrical machine 14a to an output.
  • the planetary gear 20a has two power input sources. To the planetary gear 20a are both
  • Internal combustion engine 11a as well as the electrical machine 14a, which in particular have different ratios.
  • the internal combustion engine 1 1a and the electric machine 14a are both connected to the planetary gear 20a via the second input shaft 21a.
  • Both the internal combustion engine 11 a and the electrical machine 14 a preferably transmit their torques via the same shaft, namely the input shaft 21 a, into the planetary gear 20 a.
  • a first torque flow originating from the internal combustion engine 1 1a and a second torque flow originating from the electrical machine 14a are brought together and introduced into the planetary gear 20a.
  • the internal combustion engine 1 1 a is in terms of that of the internal combustion engine 1 1 a
  • the electrical machine 14a is upstream of the second torque flow originating from the electrical machine 14a
  • Input shaft 21 a arranged.
  • the internal combustion engine 1 a is the internal combustion engine 1 a
  • the gears of the planetary gear 20a by at least a first
  • the planetary gear 20a has, for example, two schematically illustrated planetary gear sets P1a, P2a.
  • the planetary gear 20a has the first planetary gear set P1a and a second planetary gear set P2a.
  • the first planetary gear set P1 a and the second planetary gear set P2a of the planetary gear 20a each have a first ring gear 30a and a second ring gear 35a, a first
  • Planet gear carrier 31a and a second planet carrier 36a as well as a first sun gear 32a and a second sun gear 37a.
  • the ring gears 30a, 35a, the planet gear carriers 31a, 36a and the sun gears 32a, 37a are also used as elements of the
  • the planetary gear 20a has two Switching units S3a, S4a, namely a third switching unit S3a and a fourth
  • the third switching unit S3a is designed as a brake, for example.
  • the third switching unit S3a is provided to connect at least one of the elements of the planetary gear 20a in a rotationally fixed manner to a housing.
  • Switching unit S4a is formed, for example, as a clutch.
  • the fourth switching unit S4a is provided to connect at least two elements of the planetary gear 20a to one another in a rotationally fixed manner.
  • a precise configuration of the planetary gear 20a can be carried out in various ways that appear useful to a person skilled in the art.
  • three gears can be shifted, for example. All gears of the planetary gear 20a can be driven purely electrically.
  • the gears of the planetary gear 20a are at least partially power shiftable among themselves.
  • spur gear 17a is in a first gear in gears one to three of the multi-speed transmission and in a second gear in gears four to six.
  • the planetary gear 20a is in the first and fourth gear of the multi-speed transmission in a first gear, in the second and fifth gear of the multi-speed transmission in a second gear and in the third and sixth gear of the multi-speed transmission in a third gear.
  • the first shift variant is particularly suitable for a narrowly graduated planetary gear 20a with primarily at least three gears.
  • the spur gear 17a is in the first, third and fifth gears of the multi-speed transmission in a first gear and in the second, fourth and sixth gears of the multi-speed transmission in a second gear.
  • the planetary gear 20a is in gears one and two of the multi-speed transmission in a first gear, in gears three and four of the multi-speed transmission in a second gear and in gears five and six in a third gear
  • Circuit variant is particularly suitable for a widely stepped planetary gear 20a with primarily two gears.
  • the hybrid drive system 10a also has an axle drive 23a.
  • the axle gear 23a is directly coupled to the output shaft 22a of the planetary gear 20a.
  • the output shaft 22a is preferably connected in a rotationally fixed manner to a differential cage of the axle drive.
  • the output shaft 22a is also non-rotatable with at least one of the elements of the planetary gear 20a connected. Starting from the planetary gear 20a, torques can thus be introduced into the output shaft 22a, these torques being passed on from the output shaft 22a into the axle gear 23a.
  • axle gear 23a is coaxial with the second input shaft 21a of the
  • the input shaft 21 is particularly preferably designed as a hollow shaft within which at least sections of at least one side shaft 27a is arranged.
  • the planetary gear 20a is coaxial with that
  • the planetary gear 20a is arranged coaxially with the axle gear 23.
  • the first planetary gear set P1a is arranged coaxially with the axle gear 23a.
  • Planetary gear set P1a is arranged coaxially to the side shafts 27a, 28a.
  • the axle drive 23a is particularly preferably designed as a ball differential and arranged radially within the first planetary gear set P1a.
  • the first planetary gear set P1 a is particularly preferably arranged radially surrounding and axially at least partially overlapping to the axle drive 23 a.
  • the first sun gear 32a, the first planet gear carrier 31a and the first ring gear 30a are preferably radially surrounding and axial
  • the axle gear 23a is also axially parallel and axially offset to the first
  • the axle drive 23a is provided to transmit a force on the side shafts 27a, 28a from the internal combustion engine 1 1a or the electric machine 14a to the multi-speed transmission
  • crankshaft 12a of the internal combustion engine 1 1a, the rotor 15a of the electrical machine 14a and the second input shaft 21a of the planetary gear 20a are arranged axially parallel and offset from one another.
  • the crankshaft 12a of the internal combustion engine 1 1a, the rotor 15a of the electrical machine 14a and the second input shaft 21a of the planetary gear 20a are arranged axially parallel and offset from one another.
  • Planetary gear 20a are arranged axially parallel and offset from one another.
  • the axis offset between the electrical machine 14a and the planetary gear 20a is generated via at least one spur gear.
  • the axis offset could also be generated by a chain.
  • FIGS. 2 to 4 show three further exemplary embodiments of the invention. The following descriptions are essentially limited to the differences between the exemplary embodiments, with respect to the same components,
  • FIG. 1 Exemplary embodiments, in particular FIG. 1, are referred to.
  • FIG. 2 schematically shows a hybrid drive system 10b for a motor vehicle.
  • the hybrid drive system 10b has an internal combustion engine 11b.
  • the hybrid drive system 10b also has an electric drive unit 13b.
  • the electric drive unit 13b has an electric machine 14b which has a rotor 15b.
  • the electrical machine 14b has a stator 16b.
  • the electric machine 14b is on a side of the internal combustion engine 11b
  • Hybrid drive system 10b arranged.
  • the hybrid drive system 10b also has a multi-speed transmission.
  • the hybrid drive system 10b has a spur gear 17b.
  • the hybrid drive system 10b also has a planetary gear 20b.
  • the spur gear 17b has a first input shaft 18b and a first
  • the spur gear 17a also has a second one
  • crankshaft 12b of the internal combustion engine 11b can be coupled in a rotationally fixed manner to the first input shaft 18b.
  • Helical gear 17b is arranged coaxially with crankshaft 12b of internal combustion engine 11b. Furthermore, the first countershaft 19b, the second countershaft 25b and the crankshaft 12b are arranged axially parallel to one another. The first countershaft 19b, the second countershaft 25b and the crankshaft 12b are arranged axially parallel and offset from one another.
  • the hybrid drive system 10b has one
  • Torsional damper 26b which is arranged between the input shaft 18b and the crankshaft 12b and connects them.
  • the torsion damper 26b is arranged axially between the internal combustion engine 11b and the spur gear 17b.
  • the spur gear 17b has exactly two switchable spur gear pairs V1 b, V2b, and a first switchable spur gear pair V1 b and a second switchable one
  • the first switchable spur gear pair V1 b of the spur gear 17b has a first input shaft gear V11 b, which is arranged coaxially to the first input shaft 18b of the spur gear 17b.
  • the first input shaft gear V11 b is arranged on the first input shaft 18b.
  • the first input shaft gear V1 1b is formed by a fixed gear of the first input shaft 18b.
  • Spur gear pairing V1 b of the spur gear 17b has a first countershaft gear V12b, which is arranged coaxially to the first countershaft 19b of the spur gear 17b.
  • the first countershaft gear V12b is on the first countershaft 19b
  • the first countershaft gear V12b is of an idler gear of the first
  • the first input shaft gear V1 1 b meshes directly with the first countershaft gear V12b.
  • the first switchable spur gear pair V1 b is arranged in a first gear plane Z1 b.
  • the second switchable spur gear pair V2b of the spur gear 17b has a second countershaft gear V22b, which is arranged coaxially to the second countershaft 25b of the spur gear 17b.
  • the second countershaft gear V22b is arranged on the second countershaft 25b.
  • the second countershaft gear V22b is formed by an idler gear of the second countershaft 25b.
  • the second countershaft gear V22b meshes directly with the first input shaft gear V11b of the first switchable spur gear pairing V1a.
  • the first input shaft gear V11 b is assigned to the first switchable spur gear pair V1 a and the second switchable spur gear pair V2a.
  • the second spur gear pair V2b is also arranged in the first gear plane Z1 b.
  • the first switchable spur gear pair V1b of the spur gear 17b has a first switching unit S1 b with a first switching element S11 b.
  • the first switching element S1 1 b is provided for releasable coupling of the first countershaft gear V12b to the first countershaft 19b.
  • the first switching element S11 b is arranged coaxially with the first countershaft 19b.
  • the second switchable spur gear pair V2b of the spur gear 17b has a second switching unit S2b with a second switching element S21 b.
  • the second switching element S21b is provided for releasable coupling of the second countershaft gear V22b to the second countershaft 25b.
  • the second switching element S21 b is arranged coaxially with the second countershaft 25b.
  • the spur gear 17b has an output V3b.
  • the output V3b is formed by an output spur gear pair.
  • the output V3b has a first output gear V31 b, which is arranged coaxially with the first countershaft 19b of the spur gear 17b.
  • the first driven gear V31b is arranged on the first countershaft 19b.
  • the first driven gear V31 b is formed by a fixed gear of the first countershaft 19b.
  • the first driven gear V31 b is assigned to the first countershaft 19b.
  • the output V3b has a second output gear V32b, which is arranged coaxially with the second countershaft 25b of the spur gear 17b.
  • the second driven gear V32b is arranged on the second countershaft 25b.
  • Output gear V32b is formed by a fixed gear of the second countershaft 25b.
  • the second driven gear V32b is assigned to the second countershaft 25b.
  • the output V3b of the spur gear 17b has a first input shaft gear V33b, which is arranged coaxially with a second input shaft 21b of the planetary gear 20b.
  • the first input shaft gear V33b is arranged on the second input shaft 21b.
  • the first input shaft gear V33b is formed by a fixed gear of the second input shaft 21b.
  • the first driven gear V31 b and the second driven gear V32b each mesh directly with the first input shaft gear V33b.
  • the output V3b of the spur gear 17b is arranged in a second gear plane Z2b.
  • the first driven gear V31b and and the second driven gear V32b are arranged in the second gear plane Z2b.
  • the exactly two switchable spur gear pairs V1 b, V2b of the spur gear 17b are arranged in the torque flow before the output V3b.
  • the output V3b forms an output of the spur gear 17b for the two switchable spur gear pairs V1 b, V2b.
  • the electric drive unit 13b has a spur gear pair V4b.
  • the rotor 15b of the electrical machine 14b can be coupled to the second input shaft 21b of the planetary gear 20b via the spur gear pair V4b.
  • Helical gear pair V4b the rotor 15b of the electrical machine 14b is permanently coupled to the second input shaft 21b of the planetary gear 20b.
  • the spur gear pair V4b of the electric drive unit 13b is in a third gear plane Z3a
  • the planetary gear 20b is arranged behind the output V3b in the torque flow.
  • the planetary gear 20b has the second input shaft 21b and an output shaft 22b.
  • the planetary gear 20b is provided for transmitting a torque of the internal combustion engine 11b transmitted via the spur gear 17b and / or from the electric machine 14b to an output.
  • the hybrid drive system 10 also has an axle drive 23b.
  • the axle gear 23b is directly coupled to the output shaft 22b of the planetary gear 20b.
  • the planetary gear 20b and the axle gear 23b are arranged coaxially to one another.
  • the properties of the planetary gear 20a and the mentioned in Figure 1 are arranged coaxially to one another.
  • Axle gear 23a also apply to the planetary gear 20b or the axle gear 23b shown in FIG.
  • crankshaft 12b of the internal combustion engine 11b, the rotor 15b of the electrical machine 14b and the second input shaft 21b of the planetary gear 20b are arranged axially parallel and offset from one another.
  • Internal combustion engine 11b, the first countershaft 19b of the spur gear 17b, the second countershaft 19b of the spur gear 17b, the rotor 15b of the electrical machine 14b and the second input shaft 21b of the planetary gear 20b are arranged axially parallel and offset from one another.
  • FIG. 3 schematically shows a hybrid drive system 10c for a motor vehicle.
  • the hybrid drive system 10c has an internal combustion engine 11c.
  • the hybrid drive system 10c also has an electric drive unit 13c.
  • the electric drive unit 13c has an electric machine 14c which has a rotor 15c.
  • the electrical machine 14c has a stator 16c.
  • the electrical machine 14c is on a side of the internal combustion engine 11c
  • Hybrid drive system 10c arranged.
  • the hybrid drive system 10c also has a multi-speed transmission.
  • the hybrid drive system 10c has a spur gear 17c.
  • the hybrid drive system 10c also has a planetary gear 20c.
  • the spur gear 17c has a first input shaft 18c and a first
  • the spur gear 17c has a second one
  • crankshaft 12c of the internal combustion engine 11c can be coupled in a rotationally fixed manner to the first input shaft 18c.
  • Helical gear 17c is arranged coaxially to the crankshaft 12c of the internal combustion engine 1 1 c. Furthermore, the first countershaft 19c, the second countershaft 25c and the crankshaft 12c are arranged axially parallel to one another. The first countershaft 19c, the second countershaft 25c and the crankshaft 12c are arranged axially parallel and offset from one another.
  • the hybrid drive system 10c has a torsion damper 26c, which is arranged between the input shaft 18c and the crankshaft 12c and this connects. The torsion damper 26c is seen axially between the
  • the spur gear 17c has exactly two switchable spur gear pairs V1 c, V2c, namely a first switchable spur gear pair V1c and a second switchable spur gear pair V2c.
  • the first switchable spur gear pair V1c of the spur gear 17c has a first input shaft gear V1 1c, which is arranged coaxially to the first input shaft 18c of the spur gear 17c.
  • the first input shaft gear V11c is arranged on the first input shaft 18c.
  • the first input shaft gear V11c is formed by a fixed gear of the first input shaft 18c. Furthermore, the first switchable
  • the first countershaft gear V12c is on the first countershaft 19c
  • the first countershaft gear V12c is formed by an idler gear of the first countershaft 19c.
  • the first input shaft gear V11c meshes directly with the first countershaft gear V12c.
  • the first switchable spur gear pairing V1c is arranged in a first gearwheel plane Z1c.
  • the second switchable spur gear pair V2c of the spur gear 17c has a second countershaft gear V22c, which is arranged coaxially to the second countershaft 25c of the spur gear 17c.
  • the second countershaft gear V22c is arranged on the second countershaft 25c.
  • the second countershaft gear V22c is formed by an idler gear of the second countershaft 25c.
  • the second countershaft gear V22c meshes directly with the first input shaft gear V11c of the first switchable spur gear pairing V1a.
  • the first input shaft gear V1 1c is assigned to the first switchable spur gear pair V1a and the second switchable spur gear pair V2a.
  • the second spur gear pairing V2c is also arranged in the first gear plane Z1c.
  • the first switchable spur gear pair V1c of the spur gear 17c and the second switchable spur gear pair V2c of the spur gear 17c are arranged in a common gear plane, namely the gear plane Z1c.
  • the first switchable spur gear pair V1c of the spur gear 17c has a first switching unit S1 c with a first switching element S11c.
  • the first switching element S1 1c is provided for releasable coupling of the first countershaft gear V12c to the first countershaft 19c.
  • the first switching element S1 1c is coaxial with the first Layshaft 19c arranged.
  • the second switchable spur gear pair V2c of the spur gear 17c has a second switching unit S2c with a second switching element S21 c.
  • the second switching element S21c is provided for releasable coupling of the second countershaft gear V22c to the second countershaft 25c.
  • the second switching element S21c is arranged coaxially with the second countershaft 25c.
  • the spur gear 17c has an output V3c.
  • the output V3c is formed by an output spur gear pair.
  • the output V3c has a first output gear V31c, which is arranged coaxially to the first countershaft 19c of the spur gear 17c.
  • the first driven gear V31c is arranged on the first countershaft 19c.
  • the first driven gear V31c is formed by a fixed gear of the first countershaft 19c.
  • the first driven gear V31 c is assigned to the first countershaft 19c.
  • the output V3c has a second output gear V32c, which is coaxial with the second
  • the second driven gear V32c is arranged on the second countershaft 25c.
  • the second driven gear V32c is formed by a fixed gear of the second countershaft 25c.
  • the second driven gear V32c is assigned to the second countershaft 25c.
  • Helical gear 17c a first input shaft gear V33c, which is arranged coaxially to a second input shaft 21c of the planetary gear 20c.
  • Input shaft gear V33c is arranged on the second input shaft 21c.
  • the first input shaft gear V33c is formed by a fixed gear of the second input shaft 21c.
  • the first driven gear V31c and the second driven gear V32c each mesh directly with the first input shaft gear V33c.
  • the output V3c of the spur gear 17c is arranged in a second gear plane Z2c.
  • the exactly two switchable spur gear pairs V1 c, V2c of the spur gear 17c are arranged in the torque flow before the output V3c.
  • the output V3c forms an output of the spur gear 17c for the two switchable spur gear pairs V1 c, V2c.
  • the electric drive unit 13c has a spur gear pair V4c.
  • the rotor 15c of the electrical machine 14c can be coupled to the second input shaft 21c of the planetary gear 20c via the spur gear pair V4c.
  • the spur gear pair V4c of the electric drive unit 13c has a first spur gear V41 c, which is rotatably connected to the rotor 15c of the electric machine 14c.
  • the first spur gear V41c meshes directly with the first output gear V31c of the output V3c. It would be however, it is also conceivable that the first spur gear V41c meshes directly with the second output gear V32c of the output V3c or the first input shaft gear V33c of the output V3c.
  • the spur gear pair V4c of the electric drive unit 13c is also arranged in the second gear plane Z2c.
  • the driven gear V31c of the first countershaft 19c and the driven gear V32c of the second countershaft 25c are arranged in the gear plane Z2c with the spur gear pairing V4c of the electric drive unit 13c.
  • the planetary gear 20c is arranged behind the output V3c in the torque flow.
  • the planetary gear 20c has the second input shaft 21c and an output shaft 22c.
  • the planetary gear 20c is provided for transmitting a torque of the internal combustion engine 11c transmitted via the spur gear 17c and / or from the electric machine 14c to an output.
  • the hybrid drive system 10c also has an axle drive 23c.
  • the axle gear 23c is directly coupled to the output shaft 22c of the planetary gear 20c.
  • the planetary gear 20c and the axle gear 23c are arranged coaxially with one another.
  • the properties of the planetary gear 20a and the mentioned in Figure 1 are arranged coaxially with one another.
  • Axle gear 23a also apply to the planetary gear 20c or the axle gear 23c shown in FIG.
  • crankshaft 12c of the internal combustion engine 11c, the rotor 15c of the electric machine 14c and the second input shaft 21c of the planetary gear 20c are arranged axially parallel and offset from one another.
  • FIG. 4 schematically shows a hybrid drive system 10d for a motor vehicle.
  • the hybrid drive system 10d has an internal combustion engine 11d.
  • the hybrid drive system 10d also has an electric drive unit 13d.
  • the electrical drive unit 13d has an electrical machine 14d which has a rotor 15d.
  • the electrical machine 14d has a stator 16d.
  • the electrical machine 14d is on a side of the internal combustion engine 11d Hybrid drive system 10d arranged.
  • the hybrid drive system 10d also has a multi-speed transmission.
  • the hybrid drive system 10d has a spur gear 17d.
  • the hybrid drive system 10d also has a planetary gear 20d.
  • the spur gear 17d has a first input shaft 18d and a first
  • the crankshaft 12d of the internal combustion engine 11d can be coupled in a rotationally fixed manner to the first input shaft 18d.
  • the hybrid drive system 10d has a torsion damper 26d, which is arranged between the input shaft 18d and the crankshaft 12d and connects them.
  • the torsion damper 26d is arranged axially between the internal combustion engine 11d and the spur gear 17d.
  • the spur gear 17d has exactly two switchable spur gear pairs V1d, V2d, namely a first switchable spur gear pair V1d and a second switchable one
  • the first switchable spur gear pair V1d of the spur gear 17d has a first input shaft gear V1 1d, which is arranged coaxially to the first input shaft 18d of the spur gear 17d.
  • the first input shaft gear V11d is arranged on the first input shaft 18d.
  • the first input shaft gear V11d is formed by a first fixed gear of the first input shaft 18d.
  • the first switchable spur gear pair V1d of the spur gear 17d has a first countershaft gear V12d, which is arranged coaxially to the first countershaft 19d of the spur gear 17d.
  • the first countershaft gear V12d is on the first countershaft 19d
  • the first countershaft gear V12d is of an idler gear of the first
  • the first input shaft gear V11d meshes directly with the first countershaft gear V12d.
  • the first switchable spur gear pair V1 d is arranged in a first gear plane Z1d.
  • the second switchable spur gear pair V2d of the spur gear 17d has a second input shaft gear V21d, which is arranged coaxially to the first input shaft 18d of the spur gear 17d.
  • the second input shaft gear V21d is arranged on the first input shaft 18d.
  • the second input shaft gear V21d is formed by a second fixed gear of the first input shaft 18d.
  • the second switchable spur gear pair V2d of the spur gear 17d has a second one
  • Lay shaft gear V22d which is arranged coaxially to the first lay shaft 19d of the spur gear 17d.
  • the second countershaft gear V22d is arranged on the first countershaft 19d.
  • the second countershaft gear V22d is formed by an idler gear of the first countershaft 19d.
  • the second input shaft gear V21d meshes directly with the second countershaft gear V22d.
  • Helical gear pairing V2d is arranged in a third gear plane Z3d.
  • the first switchable spur gear pair V1 d of the spur gear 17d has a first switching unit S1d with a first switching element S11d.
  • the first switching element S1 1d is provided for releasable coupling of the first countershaft gear V12d to the first countershaft 19d.
  • the second switchable spur gear pair V2d of the spur gear 17d has a second switching unit S2d with a second switching element S21d.
  • the second switching element S21d is provided for releasable coupling of the second countershaft gear V22d to the first countershaft 19d.
  • the first switching element S11d and the second switching element S21d are also arranged coaxially with the first countershaft 19d.
  • the spur gear 17d has an output V3d.
  • the output V3d is formed by an output spur gear pair.
  • the output V3d has a first output gear V31d, which is arranged coaxially to the first countershaft 19d of the spur gear 17d.
  • the first driven gear V31d is arranged on the first countershaft 19d.
  • the first driven gear V31d is the first of a third fixed gear
  • the output V3d of the spur gear 17d has a first input shaft gear V33d, which is arranged coaxially with a second input shaft 21d of the planetary gear 20d.
  • the first input shaft gear V33d is arranged on the second input shaft 21d.
  • the first input shaft gear V33d is formed by a fixed gear of the second input shaft 21d.
  • the first driven gear V31d meshes directly with the first input shaft gear V33d.
  • the output V3d of the spur gear 17d is arranged in a second gear plane Z2d.
  • the exactly two switchable spur gear pairs V1d, V2d of the spur gear 17d are arranged in the torque flow before the output V3d.
  • the output V3d forms an output of the spur gear 17d for the two switchable spur gear pairs V1d, V2d.
  • the electric drive unit 13d has a spur gear pair V4d.
  • the rotor 15d of the electrical machine 14d can be coupled to the second input shaft 21d of the planetary gear 20d via the spur gear pairing V4d.
  • Helical gear pairing V4d the rotor 15d of the electrical machine 14d is permanently coupled to the second input shaft 21d of the planetary gear 20d.
  • the spur gear pairing V4d of the electric drive unit 13d is in a third gear plane Z3a
  • the planetary gear 20d is arranged behind the output V3d in the torque flow.
  • the piano gear 20d has the second input shaft 21d and an output shaft 22d.
  • the planetary gear 20d is provided for transmitting a torque of the internal combustion engine 11d transmitted via the spur gear 17d and / or from the electric machine 14d to an output.
  • the hybrid drive system 10d also has an axle drive 23d.
  • the axle gear 23d is directly coupled to the output shaft 22d of the planetary gear 20d.
  • the planetary gear 20d and the axle gear 23d are arranged coaxially to one another.
  • the properties of the planetary gear 20a and the mentioned in Figure 1 are arranged coaxially to one another.
  • Axle gear 23a also apply to the planetary gear 20d or the axle gear 23d shown in FIG.
  • crankshaft 12d of the internal combustion engine 11d, the rotor 15d of the electrical machine 14d and the second input shaft 21d of the planetary gear 20d are arranged axially parallel and offset from one another.
  • Internal combustion engine 1 1d, the first countershaft 19d of the spur gear 17d, the second countershaft 19d of the spur gear 17d, the rotor 15d of the electric machine 14d and the second input shaft 21d of the planetary gear 20d are arranged axially parallel and offset from one another.

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

Abstract

L'invention concerne un système de propulsion hybride comportant un moteur à combustion interne (11a ; 11b ; 11c ; 11d) comportant un vilebrequin (12a ; 12b ; 12c ; 12d) une unité de commande électrique (13a ; 13b ; 13c) ; 13d) comportant une machine électrique (14a ; 14b ; 14b ; 14c ; 14d) ayant un rotor (15a ; 15b ; 15c ; 15d) et un stator (16a ; 16b ; 16c ; 16d), un engrenage droit (17a ; 17b ; 17c ; 17d) comportant un premier arbre d'entrée (18a ; 18b ; 18c ; 18d), un premier arbre de renvoi (19a ; 19b ; 19c ; 19d) et un arbre de sortie (V3a ; V3b ; V3c ; V3c ; V3d), un engrenage planétaire (20a ; 20b ; 20c ; 20d) ayant un deuxième arbre d'entrée (21a ; 21b ; 21c ; 21d) et un arbre de sortie (22a ; 22b ; 22c ; 22c ; 22d), et une transmission d'essieu (23a ; 23b ; 23c ; 23d), le vilebrequin (12a ; 12b ; 12c ; 12c ; 12d) du moteur à combustion interne (11a ; 11b ; 11c ; 11d) étant fixé en rotation au premier arbre d'entrée (18a ; 18b) ; 18c ; 18d), l'unité d'entraînement électrique (13a ; 13b ; 13c ; 13d) comportant une paire d'engrenages droits (V4a ; V4b ; V4c ; V4c ; V4d) par laquelle le rotor (15a ; 15b ; 15c ; 15d) de la machine électrique (14a ; 14b ; 14c ; 14c ; 14d) peut être couplé au deuxième arbre d'entrée (21a ; 21b ; 21c ; 21c ; 21d) de l'engrenage planétaire (20a ; 20b ; 20c ; 20c ; 20d), l'engrenage droit (17a ; 17b ; 17c ; 17d) pouvant être couplé au deuxième arbre d'entrée (21a ; 21b ; 21b ; 21c ; 21d) du pignon planétaire (20a ; 20b ; 20c ; 20d) en relation avec un pignon droit (17a ; 17b ; 17c ; 17d) qui est commandé par 11b ; 11c ; 11d) vers la transmission d'essieu (23a ; 23b ; 23c ; 23d) avant la sortie (V3a ; V3b ; V3c ; V3c ; V3d) exactement deux paires de pignons droits commutables (V1a, V2a ; V1b, V2b ; V1c, V2c) ; V1d, V2d) et un premier jeu d'engrenages planétaires (P1a, P1b, P1c, P1d) de l'engrenage planétaire (20a ; 20b ; 20c ; 20d) étant disposé coaxialement aux arbres latéraux (27a ; 28a ; 28b ; 27b ; 28b ; 27c ; 27c ; 28c ; 27d ; 28d ; 28d) de la transmission d'essieu (23a ; 23b ; 23c ; 23d).
PCT/EP2019/065814 2018-06-26 2019-06-17 Système de propulsion hybride WO2020002013A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201980042997.8A CN112384398A (zh) 2018-06-26 2019-06-17 混动式动力传动系

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018005034.4 2018-06-26
DE102018005034.4A DE102018005034B4 (de) 2018-06-26 2018-06-26 Hybridantriebssystem

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WO2020002013A1 true WO2020002013A1 (fr) 2020-01-02

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DE (1) DE102018005034B4 (fr)
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CN112895878A (zh) * 2021-03-26 2021-06-04 重庆青山工业有限责任公司 纵置双电机混合动力传动装置

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