WO2016046001A1 - Antriebsanordnung und verfahren zum betrieb einer antriebsanordnung - Google Patents
Antriebsanordnung und verfahren zum betrieb einer antriebsanordnung Download PDFInfo
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- WO2016046001A1 WO2016046001A1 PCT/EP2015/070931 EP2015070931W WO2016046001A1 WO 2016046001 A1 WO2016046001 A1 WO 2016046001A1 EP 2015070931 W EP2015070931 W EP 2015070931W WO 2016046001 A1 WO2016046001 A1 WO 2016046001A1
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- 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
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- 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
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- 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
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- 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
- B60K6/26—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 motors or the generators
- B60K2006/268—Electric drive motor starts the engine, i.e. used as starter motor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
- B60K2006/4808—Electric machine connected or connectable to gearbox output shaft
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- 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
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- 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
- B60K2006/4833—Step up or reduction gearing driving generator, e.g. to operate generator in most efficient speed range
- B60K2006/4841—Step up or reduction gearing driving generator, e.g. to operate generator in most efficient speed range the gear provides shifting between multiple ratios
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- 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 present invention relates to a drive arrangement for a motor vehicle comprising a first drive unit, a second drive unit and an output unit, and a method for operating a drive arrangement.
- hybrid drives usually comprise two drive units, an electric machine and an internal combustion engine, which are coupled to one another via a torque transmission or superposition unit.
- the drive powers of the two drive machines or the respective drive torques are summed up by means of the torque transfer or superimposition unit, i. superimposed. This is done e.g. by means of a summing gear.
- the hybrid drive comprises a first drive machine and a second drive machine, which are coupled to one another via a summation gear.
- the first drive machine an electric machine, is coupled or coupleable via a first torque input to a first ratio device and the second drive unit, an internal combustion engine, to a second ratio device of the summing gear via a second torque input.
- At least one, preferably Both translation facilities have at least two alternatively selectable translations or translation levels.
- the first drive machine can be coupled via the first transmission device and the second drive machine can be coupled via the second transmission device to a common output shaft, wherein an output spur gear is arranged on the output shaft and transmits the torque of the first drive unit and / or the second drive unit to a driven output shaft. Differential transmits. The summation takes place here on an output shaft with a Abtriebsstirnrad towards a driven differential. It is in a first aspect an object of the invention to provide an alternative to the known solutions, compact and inexpensive drive arrangement. In a second aspect, it is an object of the invention to improve a method of operating a drive assembly in relation to the known methods. This object is achieved in the first aspect by the features mentioned in claim 1.
- the drive arrangement according to the invention comprises a first drive unit which can be coupled to the output unit via a first transmission assembly having an output unit and a second drive unit which can be coupled to the output unit via a second transmission assembly.
- the drive torque or the drive power of the first drive unit can be transmitted to the output unit independently of the second drive unit via the first transmission assembly.
- the drive torque or the drive power of the second drive unit can be transmitted to the output unit independently of the first drive unit via the first transmission assembly.
- first and the second gear assembly can be operated and switched independently of each other.
- the drive torque or the drive power of the first drive unit via the first gear assembly and the second drive unit via the second gear assembly to the output unit is also simultaneously transferable.
- the first drive unit and the second Drive unit can be operated in this case, if necessary, each with maximum drive power.
- each transmission elements are provided on the transmission assemblies, which cooperate with a transmission element of the output unit.
- the transmission elements are preferably intermeshing gears / pinions. This design allows both power paths to be independently optimized for maximum performance.
- the first gear assembly and the second gear assembly are non-positively and / or positively connected.
- the connection of the first gear assembly and the second gear assembly is made switchable and via gears, belt and / or chain connections.
- this connection can be realized by intermeshing spur gears. This makes charging the battery at standstill and while driving possible.
- connection of the first gear assembly and the second gear assembly offers a wide range of operating possibilities of the drive assembly according to the invention, since drive torque or drive power of the first drive unit can be routed via the connection of the first gear assembly and the second gear assembly directly to the second drive unit, and vice versa.
- gear stages of the first gear assembly can be used by the second gear assembly, and vice versa. This requires a saving of necessary components.
- the first drive unit is designed as an internal combustion engine and the second drive unit as an electric machine, whereby a so-called parallel hybrid arrangement is realized. Due to the structural design of the drive assembly according to the invention, namely the independently operable transmission assemblies, it is possible the burn operating motor and the electric machine in the respective optimal and / or maximum power ranges.
- an internal combustion engine is used as the first drive unit and an electric machine is used as the second drive unit, then for example purely electric driving (drive via electric machine), hybrid driving (drive via electric machine and internal combustion engine) and a Driving by internal combustion engine possible. Due to the structural design of the drive assembly according to the invention, it is possible that the first drive unit and the second drive unit are operated at maximum output power, if required, even if the two drive units are not of the same type (for example, a combination of internal combustion engine and electric machine).
- the first drive unit can be started by means of the second drive unit, or vice versa. This is done by the first gear assembly with the second gear assembly is positively and / or positively connected.
- an electrical energy store is charged by means of the output power of the first drive unit by frictionally and / or positively connecting the first transmission assembly to the second transmission assembly.
- the electric machine is particularly preferably operable as a motor or generator and electrically connected to an electrical energy store.
- the electrical energy store is, for example, a secondary battery unit. If the electric machine works as a motor, the necessary energy is drawn from the electrical energy store. If the electric machine works as a generator, the electrical energy store is charged via the electric machine.
- the switchable coupling of the first gear assembly is designed as a non-power shiftable single-clutch and the switchable clutch of the second gear assembly designed as a power shift double clutch.
- the first input shaft can be connected to the first drive unit via a first clutch and / or the two second input shafts can be connected to the second drive unit via a second main clutch.
- the first gear assembly has at least one intermediate shaft of the first gear assembly and / or the second gear assembly has at least one intermediate shaft of the second gear assembly.
- the intermediate shaft of the first gear assembly is preferably parallel to the first input shaft and to the first output shaft and the intermediate shaft
- the second gear assembly is preferably arranged parallel to the second input shaft and to the second output shaft.
- the gear stages can also be arranged on intermediate shafts. The constructive use of intermediate shafts a more compact design of the drive assembly according to the invention is possible.
- the output power of the first drive unit can be transmitted via the first gear assembly to the output unit and the output power of the second drive unit transmitted via the second gear assembly to the output unit.
- the first gear assembly and thus the first drive unit and the second gear assembly and thus the second drive unit are operated individually, independently of each other or simultaneously.
- the shiftable clutch of the first gear assembly is designed as a non-power shift single clutch, so can be supported via the connection between the first gear assembly and second gear assembly by means of the drive power of the second drive unit switching the non-power shift single clutch and thus simulated a power shift clutch become.
- FIG. 1 is a schematic representation of a first embodiment of a drive arrangement according to the invention
- FIG. 2 is a schematic representation of a second embodiment of a drive arrangement according to the invention.
- FIG. 3 is a schematic representation of a third embodiment of a drive arrangement according to the invention.
- Fig. 4 is a schematic representation of a fourth embodiment
- FIG. 5 shows a schematic representation of a fifth embodiment of a drive arrangement according to the invention.
- Fig. 6 is a schematic representation of a sixth embodiment of a drive arrangement according to the invention.
- the drive arrangement A1-A6 shown schematically in FIGS. 1 to 6 essentially comprise a first drive unit 1, a first gear unit 4, a second drive unit 2, a second gear unit 5 and an output unit 3.
- the gear stages that can be represented via the gear assemblies 4, 5 can be realized.
- a plurality of gear planes are shown, each having different gear ratios.
- the gearwheels of the gear assemblies 4, 5 comprise transmission elements which usually form intermeshing gear sets, the gears being spur gears and connected respectively to input, intermediate or output shafts of the gear assembly or are made connectable.
- the wheel planes or transmission elements in the force or torque flow between the drive side and output side are einbindbar.
- the switching elements are formed depending on the arrangement or assignment to the transmission elements on two sides or on one side switchable. This is shown symbolically by the arrows S1 S2. A closer description of the switching elements does not take place at this point, as it is the expert are known. Usually, the switching elements are designed as synchronization elements.
- the first drive unit 1 is an internal combustion engine and the second drive unit 2 is an electric machine.
- the electric machine is operable as a motor or generator and is electrically connected to an electric energy storage such as a secondary battery unit. This electrical energy storage is not shown in the figure.
- the output unit 3 is a differential gear. Alternatively, the output unit may also be any other output element known to the person skilled in drive technology.
- the first and the second gear assembly 4, 5 each have at least one gear stage. The assignment and explanation of the individual gear stages is based on the description of the figures. Furthermore, each transmission assembly 4, 5 has at least one input shaft and one output shaft.
- the output shaft 8 of the first gear assembly 4 and arranged on the output shaft 8 transmission element 10 provide the connection between the first gear assembly 4 and output unit 3.
- the output shaft 9 of the second gear assembly 5 and arranged on the output shaft 9 transmission element 1 1 provide the connection between the second Gear unit 5 and output unit 3 is.
- a summation of the drive torque or the drive power of the first drive unit 1 and the second drive unit 2 takes place directly on the output unit 3.
- first gear assembly 4 and the second gear assembly 5 via, for example, a gear stage of the first gear assembly 4 or the second gear assembly 5 are interconnected.
- FIG. 1 schematically shows a first embodiment of the drive arrangement A1 according to the invention.
- the first transmission assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is over here a switchable clutch 45 with the internal combustion engine drivably coupled.
- the shiftable clutch 45 is designed as a non-power-shiftable single clutch, preferably as a single-disc dry clutch or as a wet clutch or simple jaw clutch. It is in the normally energized state "normally open.”
- Parallel to the input shaft 6, an output shaft 8 is arranged, which represents the torque output of the first gear assembly.
- a shaft 7, input shafts 13, 14, an intermediate shaft 12 and an output shaft 9 of the second gear unit 5 are arranged parallel to the drive shaft 6 or to the output shaft 8.
- the shaft 7, input shafts 13, 14 and the output shaft 9 are assigned to the second gear assembly 5 and are explained in more detail at this point.
- the first gear assembly 4 has four switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are in this first embodiment of the drive assembly according to the invention as a first gear stage 15, a second gear stage 16, a third gear stage 17 and a fourth gear stage 18 executed. All gear stages of the first gear assembly 4 are designed switchable in this embodiment by means of a switching element 40, 41 of the first gear assembly 4.
- the first input shaft 6 can be coupled to the first output shaft 8 via the first gear stage 15, the second gear stage 16 and the third gear stage 17 by means of the first switching element 40 and the second switching element 41, respectively.
- the first gear stage 15 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 15a and a rotatably mounted on the first output shaft 8 idler gear 15b.
- non-rotatably mounted on a shaft designed as spur gears
- gears are referred to as fixed.
- Rotary arranged on a shaft, designed as spur gears, gears are referred to as idler gears.
- the second gear stage 16 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 16a and a rotatably mounted on the first output shaft 8 idler gear 16b.
- the double-sided switchable switching element 40 is arranged on the first output shaft 8.
- the idler gear 15b or the idler gear 16b can be coupled to the first output shaft 8, i. the switching element 40 is used depending on the switching position of producing a rotationally fixed operative connection between idler gear 15b and the first output shaft 8 or the idler gear 16b and the first output shaft. 8
- the switching element 40 can assume the following three switching positions (arrow S1):
- the third gear stage 17 is formed by a loose wheel 17a arranged rotatably on the first input shaft 6 and a fixed wheel 17b arranged rotatably on the first output shaft 8.
- the idler gear 17a can be coupled to the first input shaft 6 by means of the double-sided switchable switching element 42, i. the switching element 42 is used depending on the circuit of producing a rotationally fixed operative connection between the idler gear 17a and the first input shaft. 6
- the fourth gear stage 18 is formed via a idler gear 18a rotatably mounted on the first input shaft 6 and a idler gear 18b rotatably mounted on the second output shaft 9 of the second gear assembly 5.
- the idler gear 18b is associated with a switching element 43.
- the fourth gear stage 18 of the first gear assembly 4 in this first embodiment of the drive assembly according to the invention, the first input shaft 6 of the first gear assembly 4 can be coupled to the second output shaft 9 of the second gear assembly 5 by means of switching of the switching element 41 and the switching element 43.
- the fourth gear stage 18 thus establishes the possible connection between the first gear assembly 4 and the second gear assembly 5, wherein the first input shaft 6 of the first gear assembly 4 can be coupled to the second output shaft 9 of the second gear assembly 5. Due to this possible connection, the fourth gear stage (4th gear) can also be used to charge the battery.
- the switching element 41 can assume the following three switching positions:
- the switching element 43 is arranged on the second output shaft 9 of the second Getriebebaugrup- pe 5 and can take the following two switching positions:
- the output shaft 8 together with a transmission element 10 designed as a spur gear or as a pinion, forms the torque output of the first gear assembly 4.
- the first drive unit 1 assignable first gear assembly 4 comprises four gear stages - the first gear stage 15, the second gear wheel 16, the third gear stage 17, the fourth gear stage 18, all gear stages are switchable and each one gear of the first drive unit 1 are assignable (VKM gear).
- the second transmission assembly 5 is designed as a dual-clutch transmission and has a torque input and a torque output.
- the dual-clutch transmission is specified for operation in two directions, since no reverse gear is provided, but the rearward movement is purely electric.
- the electric motor of the second drive unit 2 has a rotor shaft, which is coupled to the torque input of the transmission assembly 5.
- the torque input comprises a shaft 7, which is coupled via a non-switchable fifth gear stage 19 with the first intermediate shaft 12.
- the fourth gear stage 19 is formed via a non-rotatably mounted on the shaft 7 fixed gear 19a, an intermediate element 19b and a non-rotatably mounted on the first intermediate shaft 12 fixed gear 19c.
- the shaft 7 is arranged in parallel with the intermediate shaft 12, the output shaft 9, the output shaft 8 and the first input shaft 6.
- the arrangement of the intermediate shaft 12 can be dispensed with. This eliminates the gear stage 19.
- the shaft 7 is connected directly to the clutch housing 48a.
- the gear assembly 5 has two gear assembly 5a, 5b, which each have an input shaft 13, 14 assigned.
- the input shafts 13, 14 can be coupled via a double clutch 48 to the torque input (shaft 7) of the second drive unit 2.
- the double clutch usually consists of two concentrically arranged clutches K1, K2 and the clutch clutches / clutch housing 48a surrounding the two clutches K1, K2.
- the clutch housing 48 a is connected to the intermediate shaft 12.
- Each clutch K1 or K2 can switch a connection to an input shaft 13, 14.
- the actuation of the clutches K1, K2 is independent.
- One clutch serves a number of even gears, the other clutch the number of odd gears.
- the first gear or the seventh gear stage 21 is assigned to the input shaft 14 designed as a solid shaft.
- the second input shaft 13 is designed as a hollow shaft, which is arranged concentrically to the first input shaft 14.
- the second input shaft 13 is associated with the sixth gear stage 20.
- Parallel to the input shafts 13, 14, an output shaft 9 is arranged, which is the torque forms output.
- the intermediate shaft 12 and the two input shafts 13, 14 are arranged coaxially.
- the gear / fixed gear 20a of the sixth gear stage 20 is arranged rotationally fixed.
- the gear / idler gear 18b of the gear stage 20 is rotatably mounted on the output shaft 9.
- the idler gear 18b can be coupled to the output shaft 9 by means of switching of the switching element 43 which can be switched on one side.
- the switching element 43, the clutch K1, the intermediate shaft 12, the input shaft 13 and the output shaft 9 are drive-coupled.
- the gear / fixed gear 21 a of the seventh gear stage 21 is arranged rotationally fixed.
- the gear / idler gear 21 b of the seventh gear stage 21 is rotatably mounted on the output shaft 9.
- the idler gear 21 b is coupled by means of switching a one-sided switching element 44 with the second output shaft 9.
- the switching element 44 is arranged on the second output shaft 9 of the second gear assembly 5 and can assume the following two switching positions:
- the sixth gear stage 20 is thus formed via a non-rotatably mounted on the input shaft 13 fixed gear 20a and a rotatably mounted on the output shaft 9 idler gear 18b.
- the seventh gear stage 21 is formed via a fixedly arranged on the input shaft 14 fixed gear 21 a and a rotatably mounted on the output shaft 9 idler gear 21 b.
- the sixth gear stage 20 is designed to be switchable via the clutch K2 of the dual clutch 48.
- the seventh gear stage 21 is designed to be switchable via the clutch K1 of the dual clutch 48.
- the double clutch 48 and can take the following three switching positions:
- the second drive unit 2 assignable to the second drive unit 5 comprises a total of three gear stages - the fifth gear stage 19, the sixth gear stage 20 and the seventh gear stage 21st
- the sixth gear stage 20 and the seventh gear stage 21 are designed to be power-shiftable by means of the double clutch 42 and can each be assigned to one gear of the second drive unit 2 (EM gear).
- the second output shaft 9 and a rotatably mounted thereon second transmission element 1 1 represent the connection between the second gear assembly 5 and output unit 3.
- the first output shaft 8 and a rotatably mounted first transmission element 10 represent the connection between the first gear assembly 4 and output unit 3
- Transmission elements 10, 1 1 are here spur gears, which engage in a rotatably mounted on an input shaft 38 of the output unit 3 spur gear 39. A summation of the drive torque or the drive power of the first drive unit 1 and the second drive unit 2 takes place directly on the output unit 3.
- FIG. 2 schematically shows a first embodiment of the drive arrangement A2 according to the invention.
- the first gear assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is in this case coupled via a switchable clutch 45 with the internal combustion engine driveable.
- the switchable clutch 45 is designed as a non-power-shiftable single clutch, preferably as Einommentrockenkupplung.
- Parallel to the input shaft 6, an output shaft 8 is arranged, which represents the torque output of the first Getriebebau- group.
- the shaft 7, input shafts 13, 14, an intermediate shaft 12 and an output shaft 9 of the second gear assembly 5 are arranged parallel to the drive shaft 6 and the output shaft 8.
- the shaft 7, input shafts 13, 14 and the output shaft 9 are associated with the second gear assembly 5 and are explained in more detail here.
- the first gear assembly 4 has four switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are designed as a first gear stage 55, a second gear stage 56, a third gear stage 57 and a fourth gear stage 58.
- the first gear stage 55 is formed via a idler gear 55a arranged rotatably on the first input shaft 6 and a idler gear 55b arranged rotatably on the second output shaft 9 of the second gear assembly 5.
- the second gear stage 56 is formed via a rotatably mounted on the first input shaft 6 idler gear 56a and a non-rotatably mounted on the first output shaft 8 fixed gear 56b.
- a two-sided switchable switching element 40 is arranged on the first input shaft 6.
- the switching element 40 By means of the switching element 40, the idler gear 55a or the idler gear 56a can be coupled to the first input shaft 6, i. the switching element 40 is used depending on the circuit of producing a rotationally fixed operative connection between idler gear 55a and 56a and the first input shaft. 6
- the switching element 40 can assume the following three switching positions:
- the switching element 40 can assume the following two switching positions:
- the first gear stage 55 thus establishes the possible connection between first gear assembly 4 and second gear assembly 5, wherein the first input shaft 6 of the first gear assembly 4 with the second output shaft 9 of the second gear assembly 5 can be coupled.
- the third gear stage 57 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 57a and a rotatably mounted on the first output shaft 8 idler gear 57b.
- the fourth gearwheel stage 58 is formed via a fixed wheel 58a, arranged rotatably on the first input shaft 6, and a loose wheel 58b arranged rotatably on the first output shaft 8.
- a switching element 41 is arranged between the idler gear 57b and the idler gear 58b.
- the switching element 41 By means of the switching element 41, the idler gear 57b or the idler gear 58b can be coupled to the first output shaft 8, i. the switching element 41 is used depending on the circuit of producing a rotationally fixed operative connection between idler gear 57b and the first output shaft 8 or the idler gear 58b and the first output shaft eighth
- the switching element 41 can assume the following three switching positions:
- the first drive unit 1 assignable first gear assembly 4 comprises a total of four gear stages - the first gear stage 55, the second gear stage 56, the third gear stage 57 and the fourth gear stage 58, wherein the first gear stage 55 and the second gear stage 56 by means of the switching element 40 and the Third gear stage 57 and the fourth gear stage 58 are designed switchable by means of the second switching element 41 of the first gear assembly 4 and each a gear of the first drive unit 1 can be assigned (VKM gear).
- the second transmission assembly 5 is designed as a dual-clutch transmission and has a torque input and a torque output.
- the electric motor of the second drive unit 2 has a rotor shaft, which is coupled to the torque input of the transmission assembly 5.
- the torque input comprises a shaft 7, which is coupled via a non-switchable fifth gear stage 59 with the first intermediate shaft 12.
- the fifth gear stage 59 is formed via a non-rotatably mounted on the shaft 7 fixed gear 59a, an intermediate element 59b and a non-rotatably mounted on the first intermediate shaft 12 fixed gear 59c.
- the shaft 7 is arranged in parallel with the intermediate shaft 12, the output shaft 9, the output shaft 8 and the first input shaft 6. As already described with reference to FIG. 1, the intermediate shaft can alternatively be dispensed with.
- the gear assembly 5 has two sub-gear assemblies 5a, 5b, which each have an input shaft 13, 14 assigned.
- the input shafts 13, 14 can be coupled via a double clutch 48 to the torque input (shaft 7, intermediate shaft 12) of the second drive unit 2.
- the double clutch usually consists of two concentrically arranged clutches K1, K2 and the clutch clutches / clutch housing 48a surrounding the two clutches K1, K2.
- the clutch housing 48 a is connected to the intermediate shaft 12.
- the intermediate shaft is designed as a hollow shaft and arranged coaxially with the input shafts 13, 14.
- Each clutch K1 or K2 can switch a connection to an input shaft 13, 14.
- the actuation of the clutches K1, K2 is independent.
- the first gear or the seventh gear stage 61 is associated with the input shaft 14 designed as a solid shaft.
- the second input shaft 13 is designed as a hollow shaft, which is arranged concentrically to the first input shaft 14.
- the first intermediate shaft 12 surrounds the input shaft 14, the input shaft 13 is arranged coaxially around the intermediate shaft 12.
- the second input shaft 13 is associated with the sixth gear stage 60.
- Parallel to the input shafts 13, 14, an output shaft 9 is arranged, which forms the torque output.
- the intermediate shaft 12 and the two input shafts 13, 14 are arranged coaxially.
- the gear / fixed gear 60a of the sixth gear stage 60 is arranged rotationally fixed.
- the gear / fixed gear 60b of the gear stage 20 is rotatably mounted on the output shaft 9.
- the gear / fixed gear 61 a of the seventh gear stage 61 is arranged rotationally fixed.
- the gear / idler gear 55b of the seventh gear stage 21 is rotatably arranged on the output shaft 9.
- the idler gear 55b can be coupled to the second output shaft 9 by means of switching of the switching element 42 which can be switched on one side.
- the sixth gear stage 60 is thus formed via a non-rotatably mounted on the input shaft 13 fixed gear 60a and a non-rotatably mounted on the output shaft 9 fixed gear 60b.
- the seventh gear stage 61 is formed via a non-rotatably mounted on the input shaft 14 fixed gear 61 a and a rotatably mounted on the output shaft 9 idler gear 55b.
- the sixth gear stage 60 is designed to be switchable via the clutch K2 of the dual clutch 48.
- the seventh gear stage 61 is designed to be switchable via the clutch K1 of the double clutch 48.
- the double clutch 48 and can take the following three switching positions:
- the second drive unit 2 assignable to the second drive unit 5 comprises a total of three gear stages - the fifth gear stage 19, the sixth gear stage 60 and the seventh gear stage 61st
- the sixth gear stage 60 and the seventh gear stage 61 are designed to be power-shiftable by means of the double clutch 48 and can each be assigned to one gear of the second drive unit 2 (EM gear).
- the second output shaft 9 and a rotatably mounted thereon second transmission element 1 1 represent the connection between the second gear assembly 5 and output unit 3.
- the first output shaft 8 and a rotatably mounted first transmission element 10 represent the connection between the first gear assembly 4 and output unit 3
- Transmission elements 10, 1 1 are here spur gears, which engage in a rotatably mounted on an input shaft 38 of the output unit 3 spur gear 39. A summation of the drive torque or the drive power of the first drive unit 1 and the second drive unit 2 takes place directly on the output unit 3.
- FIG. 3 schematically shows a third embodiment of the drive arrangement A3 according to the invention.
- the first gear assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is in this case coupled via a switchable clutch 45 with the internal combustion engine driveable.
- the switchable clutch 45 is designed as a non-power-shiftable single clutch, preferably as Einommentrockenkupplung.
- Parallel to the input shaft 6, an output shaft 8 is arranged, which represents the torque output of the first Getriebebau- group.
- the shaft 7, input shafts 13, 14, an intermediate shaft 12 and an output shaft 9 of the second gear assembly 5 are arranged parallel to the drive shaft 6 and the output shaft 8.
- the shaft 7, input shafts 13, 14 and the output shaft 9 are associated with the second gear assembly 5 and are explained in more detail here.
- the first gear assembly 4 has four switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are executed in this first embodiment of the drive assembly according to the invention as a first gear stage 65, a second gear stage 66, a third gear stage 67 and a fourth gear stage 68.
- the gear stages of the first gear assembly 4 are designed switchable by means of switching elements 40, 41 43 of the first gear assembly 4.
- the first input shaft 6 is coupled to the first output shaft 8 via the first gear stage 65, the second gear stage 66 and the third gear stage 67 by means of switching the first switching element 40 and the second switching element 41.
- the first gear stage 65 is formed by a fixed wheel 65a arranged rotatably on the first input shaft 6 and a loose wheel 65b arranged rotatably on the first output shaft 8.
- the second gear stage 66 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 66a and a rotatably mounted on the first output shaft 8 idler gear 66b.
- the switching element 41 which can be switched on both sides, is arranged on the first output shaft 8.
- the idler gear 65b or the idler gear 66b can be coupled to the first output shaft 8, i. the switching element 41 is used depending on the switching position of producing a rotationally fixed operative connection between idler gear 65b and the first output shaft 8 or the idler gear 66b and the first output shaft. 8
- the switching element 41 can assume the following three switching positions (arrow S1):
- the third gear stage 67 is formed via a rotatably mounted on the first input shaft 6 idler gear 67a and a non-rotatably mounted on the first output shaft 8 fixed gear 67b.
- the loose wheel 67a can be coupled to the first input shaft 6 by means of the double-sided switchable switching element 40, i. the switching element 40 is used depending on the circuit of producing a rotationally fixed operative connection between idler gear 67a and the first input shaft. 6
- the fourth gear stage 68 is formed via a rotatably mounted on the first input shaft 6 idler gear 68a and a rotatably mounted on the second output shaft 9 of the second gear assembly 5 idler gear 68b.
- the idler gear 68b is associated with a one-sided switchable switching element 43.
- the first input shaft 6 of the first gear assembly 4 with the second output shaft 9 of the second gear assembly 5 by means of switching the switching element 40 and the switching element 43 can be coupled.
- the fourth gear stage 68 thus establishes the possible connection between the first gear assembly 4 and the second gear assembly 5, wherein the first input shaft 6 of the first gear assembly 4 can be coupled to the second output shaft 9 of the second gear assembly 5.
- the switching element 40 can assume the following three switching positions:
- the switching element 43 is arranged on the second output shaft 9 of the second gear assembly 5 and can assume the following two switching positions: Connection of Losrad 68b with second output shaft. 9
- the output shaft 8 together with a transmission element 10 designed as a spur gear or as a pinion, forms the torque output of the first gear assembly 4.
- the first drive unit 1 assignable first gear assembly 4 comprises four gear stages - the first gear stage 65, the second gear wheel 66, the third gear stage 67, the fourth gear stage 68, all gears are switchable and each gear of the first drive unit 1 are assignable (VKM gear).
- the second transmission assembly 5 is designed as a dual-clutch transmission and has a torque input and a torque output.
- the electric motor of the second drive unit 2 has a rotor shaft, which is coupled to the torque input of the transmission assembly 5.
- the torque input in this case comprises a shaft 7, which is coupled via a non-switchable fifth gear stage 69 with the first intermediate shaft 12.
- the gear stage 69 is formed via a non-rotatably mounted on the shaft 7 fixed gear 69a, an intermediate element 69b and a non-rotatably mounted on the first intermediate shaft 12 fixed gear 69c.
- the shaft 7 is arranged in parallel with the intermediate shaft 12, the output shaft 9, the output shaft 8 and the first input shaft 6.
- the gear assembly 5 has two sub-gear assemblies 5a, 5b, which each have an input shaft 13, 14 assigned.
- the input shafts 13, 14 can be coupled via a double clutch 48 to the torque input (shaft 7, intermediate shaft 12) of the second drive unit 2.
- the double clutch usually consists of two concentrically arranged clutches K1, K2 and the clutch clutches / clutch housing 48a surrounding the two clutches K1, K2.
- the clutch housing 48 a is connected to the intermediate shaft 12.
- Each clutch K1 or K2 can switch a connection to an input shaft 13, 14.
- the Actuation of the clutches K1, K2 is independent. One clutch serves a number of even gears, the other clutch the number of odd gears.
- the first gear or the seventh gear stage 71 is associated with the input shaft 14 designed as a solid shaft.
- the second input shaft 13 is designed as a hollow shaft, which is arranged concentrically to the first input shaft 14.
- the second input shaft 13 is associated with the sixth gear stage 70.
- Parallel to the input shafts 13, 14, an output shaft 9 is arranged, which forms the torque output.
- the intermediate shaft 12 and the two input shafts 13, 14 are arranged coaxially.
- the gear / fixed gear 70 a of the sixth gear stage 70 is arranged rotationally fixed.
- the fixed gear 70b of the gear stage 70 is arranged rotatably on the output shaft 9.
- the gear / fixed gear 71 a of the seventh gear stage 71 is arranged rotationally fixed.
- the gear / idler gear 68b of the seventh gear stage 71 is rotatably mounted on the output shaft 9.
- the idler gear 68b can be coupled to the second output shaft 9 by means of a circuit of the one-sided switching element 43.
- the sixth gear stage 70 is therefore formed via a fixedly arranged on the input shaft 13 fixed gear 70a and a non-rotatably mounted on the output shaft 9 fixed gear 70b.
- the seventh gear stage 71 is formed via a non-rotatably mounted on the input shaft 14 fixed gear 71 a and a rotatably mounted on the output shaft 9 idler gear 68b.
- the sixth gear stage 70 is designed to be switchable via the clutch K2 of the dual clutch 48.
- the seventh gear stage 71 is designed to be switchable via the clutch K1 of the dual clutch 48.
- the double clutch 48 and can take the following three switching positions:
- the second drive unit 2 assignable to the second drive unit 5 comprises a total of three gear stages - the fifth gear stage 69, the sixth gear stage 70 and the seventh gear stage 71st
- the sixth gear stage 70 and the seventh gear stage 71 are designed to be power-shiftable by means of the double clutch 48 and can each be assigned to one gear of the second drive unit 2 (EM gear).
- the second output shaft 9 and a rotatably mounted thereon second transmission element 1 1 represent the connection between the second gear assembly 5 and output unit 3.
- the first output shaft 8 and a rotatably mounted first transmission element 10 represent the connection between the first gear assembly 4 and output unit 3
- Transmission elements 10, 1 1 are here spur gears, which engage in a rotatably mounted on an input shaft 38 of the output unit 3 spur gear 39. A summation of the drive torque or the drive power of the first drive unit 1 and the second drive unit 2 takes place directly on the output unit 3.
- FIG. 4 schematically shows a fourth embodiment of the drive arrangement A4 according to the invention.
- the first gear assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is in this case coupled via a switchable clutch 45 with the internal combustion engine driveable.
- the switchable clutch 45 is designed as a non-power shift single clutch.
- a shaft 7, input shafts 13, 14, an intermediate shaft 12 and an output shaft 9 of the second gear assembly 5 are arranged parallel to the drive shaft 6 and the output shaft 8.
- the shaft 7, input shafts 13, 14 and the output shaft 9 are assigned to the second gear assembly 5 and are explained in more detail at this point.
- the first gear assembly 4 has five switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are in this first embodiment of the drive assembly according to the invention as a first gear stage 75, a second gear stage 76, a third gear stage 77, a fourth gear stage 78, a fifth gear stage 79 executed.
- the first gear stage 75 is formed via a first fixed gear 75a arranged non-rotatably on the first input shaft 6 and a idler gear 75b arranged rotatably on the first intermediate shaft 12 of the second gear assembly 5.
- the first input shaft 6 of the first gear assembly 4 can be coupled to the first intermediate shaft 12 of the second gear assembly 5 by means of a switching element 42 which can be switched on one side.
- the first gear stage 75 thus establishes the possible connection between the first gear assembly 4 and the second gear assembly 5, wherein the first input shaft 6 of the first gear assembly 4 can be coupled to the first intermediate shaft 12 of the second gear assembly 5.
- This first gear stage 75 allows charging the battery at a standstill.
- the switching element 42 is arranged on intermediate shaft 12 of the first gear assembly 5 and can take the following two switching positions:
- the first input shaft 6 is coupled to the first output shaft 8 via the second gear stage 76, the third gear stage 77, the fourth gear stage 78 and the fifth gear stage 79 by means of switching the first switching element 40 and the second switching element 41.
- the second gear stage 76 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 76a and a rotatably mounted on the first output shaft 8 idler gear 76b.
- the third gear stage 77 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 77a and a rotatably mounted on the first output shaft 8 idler gear 77b.
- the double-sided switchable switching element 40 is arranged on the first output shaft 8.
- the idler gear 76b or the idler gear 77b can be coupled to the first output shaft 8, i.
- the switching element 40 serves to produce a rotationally fixed operative connection between the idler gear 76b and the first output shaft 8 or the idler gear 77b and the first output shaft 8.
- the switching element 40 can assume the following three switching positions (arrow S1):
- the fourth gear stage 78 is formed via a fixedly disposed on the first input shaft 6 fixed gear 78a and a rotatably mounted on the first output shaft 8 idler gear 78b.
- the fifth gear stage 79 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 79a and a rotatably mounted on the first output shaft 8 idler gear 79b. Between idler gear 78b and idler gear 79b, a two-sided switchable switching element 41 is assigned to the output shaft 8.
- the switching element 41 can assume the following three switching positions (arrow S2):
- the output shaft 8 together with a transmission element 10 designed as a spur gear or as a pinion, forms the torque output of the first gear assembly 4.
- the first drive unit 1 assignable first gear assembly 4 comprises a total of five gear stages - the first gear stage 75, the second gear 76, the third gear stage 77, the fourth gear stage 78 and the fifth gear stage 79, wherein the gear stages 75, 76 by means of Switching element 40 and the gear stages 78, 79 are designed switchable by means of the switching element 41 and each a gear of the first drive unit 1 can be assigned (VKM gear).
- the second transmission assembly 5 is designed as a dual-clutch transmission and has a torque input and a torque output.
- the electric motor of the second drive unit 2 has a rotor shaft, which is coupled to the torque input of the transmission assembly 5.
- the torque input in this case comprises a shaft 7, which is coupled to the intermediate shaft 12 via a non-shiftable sixth gear stage 80.
- the sixth gear stage 80 is formed via a non-rotatably mounted on the shaft 7 fixed gear 80a, an intermediate member 80b and a non-rotatably mounted on the first intermediate shaft 12 fixed gear 80c.
- the shaft 7 is arranged in parallel with the intermediate shaft 12, the output shaft 9, the output shaft 8 and the first input shaft 6.
- the gear assembly 5 has two sub-gear assemblies 5a, 5b, which each have an input shaft 13, 14 assigned.
- the input shafts 13, 14 can be coupled via a double clutch 48 to the torque input (shaft 7, intermediate shaft 12) of the second drive unit 2.
- the double clutch usually consists of two concentrically arranged clutches K1, K2 and the clutch clutches / clutch housing 48a surrounding the two clutches K1, K2.
- the clutch housing 48 a is connected to the intermediate shaft 12. Every clutch K1 or K2 can switch a connection to an input shaft 13, 14.
- the actuation of the clutches K1, K2 is independent.
- One clutch serves a number of even gears, the other clutch the number of odd gears.
- the first gear or the eighth gear stage 82 is associated with the input shaft 14 designed as a solid shaft.
- the second input shaft 13 is designed as a hollow shaft, which is arranged concentrically to the first input shaft 14.
- the second input shaft 13 is associated with the seventh gear stage 81.
- Parallel to the input shafts 13, 14, an output shaft 9 is arranged, which forms the torque output.
- the intermediate shaft 12 and the two input shafts 13, 14 are arranged coaxially.
- the gear / fixed gear 20a of the seventh gear stage 81 is arranged rotationally fixed.
- the fixed gear 81 b of the gear stage 20 is rotatably arranged on the output shaft 9.
- the clutch K1 the intermediate shaft 12, the input shaft 13 and the output shaft 9 are drive-coupled.
- the gear / fixed gear 82a of the eighth gear stage 82 is arranged rotationally fixed.
- the gear / fixed wheel 82b of the eighth gear stage 82 is arranged rotationally fixed on the output shaft 9.
- the seventh gear stage 81 is therefore formed via a non-rotatably mounted on the input shaft 13 fixed gear 81 a and a non-rotatably mounted on the output shaft 9 fixed gear 81 b.
- the eighth gear stage 82 is formed by means of a fixed wheel 82a, which is arranged rotationally fixed on the input shaft 14, and by a fixed wheel 82b, which is arranged rotatably on the output shaft 9.
- the eighth gear stage 82 is made switchable via the clutch K2 of the dual clutch 48.
- the seventh gear stage 81 is designed to be switchable via the clutch K1 of the dual clutch 48.
- the double clutch 48 and can take the following three switching positions:
- the second drive unit 2 assignable second gear assembly 5 comprises a total of three gear stages - the sixth gear stage 80, the seventh gear stage 81 and the eighth gear stage 82nd
- the seventh gear stage 81 and the eighth gear stage 82 are executed by means of the double clutch 48 and one power shift the second drive unit 2 assignable (EM-gear).
- the second output shaft 9 and a second transmission element 1 1 arranged thereon in a rotationally fixed manner form the connection between the second gear assembly 5 and the output unit 3.
- the first output shaft 8 and a first transmission element 10 arranged thereon in rotation provide the connection between the first gear assembly 4 and the output unit 3
- the transmission elements 10, 11 are spur gears which engage in a spur gear 39 arranged in a rotationally fixed manner on an input shaft 38 of the output unit 3.
- a summation of the drive torque or the drive power of the first drive unit 1 and the second drive unit 2 takes place directly on the output unit 3.
- FIG. 5 schematically shows a fifth embodiment of the drive arrangement A5 according to the invention.
- the first transmission assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is in this case coupled via a switchable clutch 45 with the internal combustion engine driveable.
- the switchable clutch 45 is designed as a non-power-shiftable single clutch, preferably as Einommentrockenkupplung.
- Parallel to the input shaft 6, an output shaft 8 is arranged, which represents the torque output of the first gear assembly.
- a shaft 7, input shafts 13, 14, an intermediate shaft 12 and an output shaft 9 of the second gear unit 5 are arranged parallel to the drive shaft 6 or to the output shaft 8.
- the shaft 7, input shafts 13, 14 and the output shaft 9 are assigned to the second gear assembly 5 and are explained in more detail at this point.
- the first gear assembly 4 has four switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are in this first embodiment of the drive assembly according to the invention as a first gear stage 85, a second gear stage 86, a third gear stage 87 and a fourth gear stage 88 executed.
- the first input shaft 6 is coupled to the first output shaft 8 via the first gear stage 85, the second gear stage 86, the third gear stage 87 and the third gear stage 88 by means of switching a switching element 40 and a switching element 41.
- the first gear stage 85 is formed via a fixedly arranged on the first input shaft 6 fixed gear 85a and a rotatably mounted on the first output shaft 8 idler gear 85b.
- the input shaft 6 of the first Getriebebaugrup- PE 4 via the fixed gear 85a with a rotatably mounted on the intermediate shaft 12 idler gear 85c coupled. This coupling is achieved by switching an arranged on the intermediate shaft 12, one-sided switchable running switching element 42.
- the switching element 42 is arranged on intermediate shaft 12 of the first gear assembly 5 and can assume the following two switching positions:
- the second gear stage 86 is formed by a fixed wheel 86a arranged rotatably on the first input shaft 6 and a loose wheel 86b arranged rotatably on the first output shaft 8.
- the double-sided switchable switching element 40 is arranged on the first output shaft 8.
- the idler gear 85b or the idler gear 86b can be coupled to the first output shaft 8, ie the switching element 40 serves, depending on the switching position, to produce a rotationally fixed active connection between idler gear 85b and the first output shaft 8 or idler gear 86b and the first output shaft 8th.
- the switching element 40 can assume the following three switching positions (arrow S1):
- the third gear stage 87 is formed via a fixedly arranged on the first input shaft 6 fixed gear 87a and a rotatably mounted on the first output shaft 8 idler gear 87b.
- the fourth gear stage 88 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 88a and a rotatably mounted on the first output shaft 8 idler gear 88b. Between idler gear 87b and idler gear 88b, a two-sided switchable switching element 41 is arranged on the output shaft 8.
- the switching element 41 can assume the following three switching positions (arrow S2):
- the first gear unit 4 to be associated with the first drive unit 4 comprises a total of four gear stages - the first gear stage 85, the second gear stage 86, the third Gear stage 87 and the fourth gear stage 88, wherein the gear stages 85, 86 by means of the switching element 40 and the gear stages 87, 88 by means of Switching element 41 are designed switchable and each a gear of the first drive unit 1 can be assigned (VKM gear)
- the second transmission assembly 5 is designed as a dual-clutch transmission and has a torque input and a torque output.
- the electric motor of the second drive unit 2 has a rotor shaft, which is coupled to the torque input of the transmission assembly 5.
- the torque input includes a shaft 7, which is coupled via a non-switchable fifth gear stage 89 with the first intermediate shaft 12.
- the fifth gear stage 89 is formed via a non-rotatably mounted on the shaft 7 fixed gear 89a, an intermediate element 89b and a non-rotatably mounted on the first intermediate shaft 12 fixed gear 89c.
- the shaft 7 is arranged in parallel with the intermediate shaft 12, the output shaft 9, the output shaft 8 and the first input shaft 6.
- the gear assembly 5 has two sub-gear assemblies 5a, 5b, which each have an input shaft 13, 14 assigned.
- the input shafts 13, 14 can be coupled via a double clutch 48 to the torque input (shaft 7, intermediate shaft 12) of the second drive unit 2.
- the dual clutch usually consists of two concentrically arranged clutches K1, K2, the housing side clutch plates and input shaft side arranged clutch plates comprise, and the two clutches K1, K2 surrounding clutch cage / clutch housing 48a.
- the clutch housing 48a is connected to the input shaft 13, wherein the input shaft 13 is designed as a hollow shaft.
- the intermediate shaft 12 is connected to the input shaft side clutch plates of the clutch K1.
- the intermediate shaft 12 is formed as a solid shaft and arranged coaxially with the input shafts 13, 14.
- the input shaft 14 is also formed as a hollow shaft and arranged coaxially about the first intermediate shaft.
- the input shaft 13 is coaxially arranged around the input shaft 14.
- the input shaft 14 is associated with the clutch K2.
- Each clutch K1 or K2 can switch a connection to an input shaft 13, 14.
- the actuation of the clutches K1, K2 is independent.
- One clutch serves a number of even gears, the other clutch the number of odd gears. From the drawing you can see that the first gear or the seventh tooth wheel step 91 is associated with the designed as a hollow shaft input shaft 14.
- the second input shaft 13 is also configured as a hollow shaft, which is arranged concentrically to the first input shaft 14.
- the second input shaft 13 is associated with the sixth gear stage 90. Parallel to the input shafts 13, 14, an output shaft 9 is arranged, which forms the torque output.
- the intermediate shaft 12 and the two input shafts 13, 14 are arranged coaxially.
- the gear / fixed gear 90a of the sixth gear stage 90 is arranged rotationally fixed.
- the gear / fixed gear 90b of the gear stage 90 is rotatably mounted on the output shaft 9.
- the gear / fixed gear 91 a of the seventh gear stage 91 is arranged rotationally fixed.
- the fixed gear 91 b of the seventh gear stage 91 is arranged rotationally fixed on the output shaft 9.
- the sixth gear stage 90 is therefore formed via a non-rotatably mounted on the input shaft 13 fixed gear 90a and a rotatably mounted on the output shaft 9 idler gear 90b.
- the seventh gear stage 91 is formed via a fixed wheel 91 a arranged non-rotatably on the input shaft 14 and a fixed wheel 91 b arranged rotatably on the output shaft 9.
- the sixth gear stage 90 is designed to be switchable via the clutch K1 of the dual clutch 48.
- the seventh gear stage 91 is designed to be switchable via the clutch K2 of the dual clutch 48.
- the double clutch 48 and can take the following three switching positions:
- the second drive unit 2 assignable second gear assembly 5 comprises a total of three gear stages - the fifth gear stage 89, the sixth gear stage 90 and the seventh gear stage 91th
- the sixth gear stage 90 and the Seventh gear stage 91 are performed by means of the double clutch 48 and shiftable each one gear of the second drive unit 2 assigned (EM-gear).
- the second output shaft 9 and a non-rotatably mounted second transmission element 1 1 represent the connection between the second gear assembly 5 and the output unit 3.
- the first output shaft 8 and a rotatably mounted first transmission element 10 provide the connection between the first gear assembly 4 and output unit 3
- the transmission elements 10, 11 are spur gears which engage in a spur gear 39 arranged in a rotationally fixed manner on an input shaft 38 of the output unit 3.
- FIG. 6 schematically shows a sixth embodiment of the drive arrangement A6 according to the invention.
- the first transmission assembly 4 has a torque input, which is designed as an input shaft 6.
- the input shaft 6 is in this case coupled via a switchable clutch 45 with the internal combustion engine driveable.
- the switchable clutch 45 is designed as a non-power-shiftable single clutch, preferably as a single-disc dry clutch.
- an input shaft 7, an intermediate shaft 12 and an output shaft 9 of the second gear assembly 5 are arranged parallel to the drive shaft 6 and the output shaft 8.
- the input shaft 7, the intermediate shaft 12, and the output shaft 9 are assigned to the second gear assembly 5 and are explained in more detail at this point.
- the first gear assembly 4 has five switchable gear stages. The assignment of the gear stages and an explanation will be given below.
- the gear stages of the first gear assembly 4 are designed as a first gear stage 95, a second gear stage 96, a third gear stage 97, a fourth gear stage 98 and a fifth gear stage 99.
- the first input shaft 6 is coupled to the first output shaft 8 via the first gear stage 95, the second gear stage 96, the third gear stage 97 and the fourth gear stage 98 by means of switching a switching element 40 and a switching element 41.
- the first gear stage 95 is formed by a fixed gear 95a, which is arranged rotatably on the first input shaft 6, and a loose gear 95b, which is rotatably arranged on the first output shaft 8.
- the second gear stage 96 is formed via a non-rotatably mounted on the first input shaft 6 fixed gear 96a and a rotatably mounted on the first output shaft 8 idler gear 96b.
- the double-sided switchable switching element 40 is arranged on the first output shaft 8.
- the switching element 40 By means of the switching element 40, the idler gear 95b or the idler gear 96b can be coupled to the first output shaft 8, i. the switching element 40 is used depending on the switching position of producing a rotationally fixed operative connection between the idler gear 95b and the first output shaft 8 or the idler gear 96b and the first output shaft eighth
- the switching element 40 can assume the following three switching positions (arrow S1):
- the third gear stage 97 is formed via a fixedly disposed on the first input shaft 6 fixed gear 97a and a rotatably mounted on the first output shaft 8 idler gear 97b.
- the fourth gear stage 98 is formed via a fixedly arranged on the first input shaft 6 fixed gear 98a and a rotatably mounted on the first output shaft 8 idler gear 98b. Between idler gear 97b and idler gear 98b, a two-sided switchable switching element 41 is arranged on the output shaft 8.
- the first input shaft 6 of the first gear assembly 4 with the first output shaft 8 by means of switching the switching element 41 can be coupled.
- the switching element 41 can assume the following three switching positions (arrow S2):
- the fifth gear stage 99 is formed via a rotatably mounted on the first input shaft 6 idler gear 99a and a non-rotatably mounted on the second input shaft 7 of the second gear assembly 5 fixed gear 99b.
- the first input shaft 6 of the first Getriebebau- group 4 with the second input shaft 7 of the second gear assembly 5 by means of switching a switching element 42 can be coupled.
- the fifth gear stage 99 thus establishes the possible connection between first gear assembly 4 and second gear assembly 5, wherein the first input shaft 6 of the first gear assembly 4 with the second input shaft 7 of the second gear assembly 5 can be coupled.
- the switching element 42 is arranged on the first input shaft 6 and designed as a one-sided switchable element and can take the following two switching positions:
- the first gear unit 4 which can be assigned to the first drive unit 1, comprises a total of five gear stages - the first gear stage 95, the second gear stage 96, the third Gear stage 97, the fourth gear stage 98 and the fifth gear stage 99, wherein the gear stages 95, 96 are designed switchable by means of the switching element 40 and the gear stages 97, 98 by means of the switching element 41 and each a gear of the first drive unit 1 can be assigned (VKM gear )
- the second gear assembly 5 is in this sixth embodiment designed as a planetary superposition unit 49, which comprises a planetary gear assembly 49a and a brake unit 49b.
- the brake unit in this case has two switching elements 43, 44, which are preferably designed as disk brakes. However, the brake unit can also be performed disc brake, band brake, etc.
- a planetary gear is the person skilled in principle known in its construction and usually consists of at least one centrally mounted on a shaft sun gear, a ring gear and a plurality of rotatably mounted on one or more planet carriers planetary wheels, which roll between sun gear and ring gear.
- the switching of the various gear ratios is done by holding or releasing one or more of the aforementioned three gear parts (sun, planet, Holhrad) z. B. by means of hydraulically operated brake bands or multi-plate clutches. Since each of the three transmission parts can be driven, driven or held, there are many possible variations.
- two planetary gear sets are connected in series / connected in parallel.
- the second input shaft 7 represents the input shaft of the planetary gear assembly 49.
- the planetary gear assembly 49 has two planetary gears P1, P2 arranged in parallel and comprises two sun gears 100, 101 arranged in a rotationally fixed manner on the second input shaft 7.
- a planet carrier 28 is rotatably arranged.
- the planet carrier has in each case to the sun gears 100, 101 facing bearing points 104, 105 for the planet gears 50, 51.
- the planet carrier 28 is designed as a spur gear. In another embodiment, instead of the spur gear and another transmission element can be used.
- the planet gears 50 of the first sun gear / planet carrier composite (planetary gear P1) are rotatably mounted on the bearings 104.
- the planet gears 51 of the second sun gear / planet carrier composite (planetary gear P1) are rotatably mounted on the bearings 105.
- the number of planet gears is variable.
- first ring gear 1 10 and the second sun gear / planet carrier composite, a second ring gear 1 1 1 associated with the first sun gear / planet carrier network Furthermore, a first ring gear 1 10 and the second sun gear / planet carrier composite, a second ring gear 1 1 1 associated with the first sun gear / planet carrier network.
- the planetary gear 49a in this sixth embodiment two switchable clutches are used, which are used as a braking element.
- the ring gears are assigned respective brake discs B1, B2, which cooperate with corresponding caliper / brake carrier arranged fixed to the housing.
- the ring gears can thus be operated free-running, be operated braked and also recorded.
- the planet carrier 28 designed as a spur gear represents the connection between the second gear assembly 5 and the output unit 3.
- the first output shaft 8 and a first transmission element 10 arranged thereon in rotation provide the connection between the first gear assembly 4 and the output unit 3.
- the transmission elements 10, 28 are spur gears which engage in a spur gear 39 fixedly arranged on an input shaft 38 of the output unit 3.
Abstract
Description
Claims
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DE112015004370.5T DE112015004370A5 (de) | 2014-09-25 | 2015-09-14 | Antriebsanordnung und Verfahren zum Betrieb einer Antriebsanordnung |
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DE102014219464 | 2014-09-25 | ||
DE102014219464.4 | 2014-09-25 |
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WO2016046001A1 true WO2016046001A1 (de) | 2016-03-31 |
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PCT/EP2015/070931 WO2016046001A1 (de) | 2014-09-25 | 2015-09-14 | Antriebsanordnung und verfahren zum betrieb einer antriebsanordnung |
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WO (1) | WO2016046001A1 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102016120010A1 (de) * | 2016-10-20 | 2018-04-26 | Getrag Ford Transmissions Gmbh | Antriebsbaugruppe mit E-Maschine für ein Kraftfahrzeug |
CN112677751A (zh) * | 2021-01-22 | 2021-04-20 | 东风汽车集团股份有限公司 | 一种基于单行星齿轮机构的单电机多档混合动力电驱系统 |
DE102020202664A1 (de) | 2020-03-02 | 2021-09-02 | Zf Friedrichshafen Ag | Getriebeanordnung für einen Hybridantrieb eines Kraftfahrzeuges |
EP4094963A1 (de) * | 2021-05-27 | 2022-11-30 | Valeo Embrayages | Hybride antriebsuntereinheit eines fahrzeugs, hybride antriebsgruppe und hybrides antriebsverfahren |
WO2023061950A1 (en) * | 2021-10-11 | 2023-04-20 | Brudeli Green Mobility As | A powertrain and a clutch-motor assembly |
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DE112005001279B4 (de) * | 2004-06-04 | 2012-02-16 | Toyota Jidosha Kabushiki Kaisha | Leistungsabgabevorrichtung und mit derselben ausgerüstetes Hybridfahrzeug |
DE102012205319A1 (de) * | 2012-04-02 | 2013-10-02 | Zf Friedrichshafen Ag | Hybridantrieb eines Kraftfahrzeugs |
DE102012016988A1 (de) * | 2012-08-25 | 2014-05-15 | Volkswagen Aktiengesellschaft | Hybridantriebsstrang für ein Kraftfahrzeug, Hybridfahrzeug und dessen Verwendung |
-
2015
- 2015-09-14 WO PCT/EP2015/070931 patent/WO2016046001A1/de active Application Filing
- 2015-09-14 DE DE112015004370.5T patent/DE112015004370A5/de not_active Withdrawn
Patent Citations (3)
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DE112005001279B4 (de) * | 2004-06-04 | 2012-02-16 | Toyota Jidosha Kabushiki Kaisha | Leistungsabgabevorrichtung und mit derselben ausgerüstetes Hybridfahrzeug |
DE102012205319A1 (de) * | 2012-04-02 | 2013-10-02 | Zf Friedrichshafen Ag | Hybridantrieb eines Kraftfahrzeugs |
DE102012016988A1 (de) * | 2012-08-25 | 2014-05-15 | Volkswagen Aktiengesellschaft | Hybridantriebsstrang für ein Kraftfahrzeug, Hybridfahrzeug und dessen Verwendung |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016120010A1 (de) * | 2016-10-20 | 2018-04-26 | Getrag Ford Transmissions Gmbh | Antriebsbaugruppe mit E-Maschine für ein Kraftfahrzeug |
DE102020202664A1 (de) | 2020-03-02 | 2021-09-02 | Zf Friedrichshafen Ag | Getriebeanordnung für einen Hybridantrieb eines Kraftfahrzeuges |
US11400804B2 (en) | 2020-03-02 | 2022-08-02 | Zf Friedrichshafen Ag | Transmission arrangement for a vehicle hybrid drive |
CN112677751A (zh) * | 2021-01-22 | 2021-04-20 | 东风汽车集团股份有限公司 | 一种基于单行星齿轮机构的单电机多档混合动力电驱系统 |
EP4094963A1 (de) * | 2021-05-27 | 2022-11-30 | Valeo Embrayages | Hybride antriebsuntereinheit eines fahrzeugs, hybride antriebsgruppe und hybrides antriebsverfahren |
FR3123283A1 (fr) * | 2021-05-27 | 2022-12-02 | Valeo Embrayages | Sous-ensemble hybride d’entraînement d’un véhicule, groupe moteur hybride et procédé d’entraînement hybride |
US11890941B2 (en) | 2021-05-27 | 2024-02-06 | Valeo Embrayages | Hybrid sub-assembly for driving a vehicle, hybrid engine unit and hybrid drive method |
WO2023061950A1 (en) * | 2021-10-11 | 2023-04-20 | Brudeli Green Mobility As | A powertrain and a clutch-motor assembly |
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DE112015004370A5 (de) | 2017-06-08 |
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