Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
  • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
  • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
  • B60K6/48—Parallel type
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
  • B60K6/54—Transmission for changing ratio
  • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
  • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
  • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/62—Gearings having three or more central gears
  • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/62—Gearings having three or more central gears
  • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
  • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
  • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
  • B60K6/48—Parallel type
  • B60K2006/4816—Electric machine connected or connectable to gearbox internal shaft
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
  • B60Y2200/00—Type of vehicle
  • B60Y2200/90—Vehicles comprising electric prime movers
  • B60Y2200/92—Hybrid vehicles
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
  • B60Y2400/00—Special features of vehicle units
  • B60Y2400/70—Gearings
  • B60Y2400/73—Planetary gearings
• • 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
  • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
  • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
  • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
• • 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
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
  • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
• • 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
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
  • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
• • 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
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
  • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/60—Other road transportation technologies with climate change mitigation effect
  • Y02T10/62—Hybrid vehicles

Definitions

• the invention relates to a transmission for a motor vehicle, as well as a drive train for a motor vehicle with such a transmission.
• a transmission referred to here in particular a multi-speed transmission in which a plurality of gears, so fixed ratios between the drive shaft and the output shaft of the transmission, are preferably automatically switched by switching elements.
• the switching elements are, for example, clutches or brakes here.
• Such transmissions are mainly used in motor vehicles to adjust the speed and torque output characteristics of the drive unit to the driving resistance of the vehicle in a suitable manner.
• Such planetary gear transmissions often have a so-called front-mounted gearset and a so-called main gearset.
• the main gearset often consists of a Planetenradsatzsystem, wherein an output shaft of the transmission is permanently connected to a shaft of the Planetenradsatzsystems.
• By acting as brakes switching elements individual shafts of the Planetenradsatzsystems are rotatably fixed, while at least one clutch, a shaft of the Planetenradsatzsystems with a drive shaft of the transmission is connectable.
• the front-mounted gearset together with other couplings, serves to provide the shafts of the main gearset with increased or reduced rotational speeds in addition to the rotational speed of the drive shaft.
• the patent application US 2013/0150196 A1 shows in FIG. 2 a transmission which has a transfer gearset designated as PGS1 and a main gearset designated PGS2.
• the transfer gearset has two planetary gear sets with a total of four shafts, wherein an electric machine is connected to one of the four shafts, and an input shaft of the transmission to a further of the four shafts.
• a brake designated CL1 By closing a brake designated CL1, a third of the four shafts can be fixed in a rotationally fixed manner. The remaining of the four shafts is covered by couplings with connectable to different waves of the main gearset.
• the brake CL1 is closed in all fixed gear ratios, as shown in FIG. 4 of said patent application, wherein, according to FIG. 18, when the brake CL1 is closed, the electric machine should turn faster than the input shaft. With the brake CL1 and another five switching elements such six forward gears can be formed.
• the transmission according to the invention has a drive shaft, an output shaft, a transfer gearset with a first and second planetary gear set, a main gearset, an electric machine with a rotationally fixed stator and a rotatable rotor and a plurality of switching elements. By selectively closing three of each of the switching elements, a plurality of fixed gear ratios between the drive shaft and the output shaft can be provided.
• the drive shaft is permanently connected to a first shaft of the transfer gear.
• the rotor of the electric machine is permanently connected to a second shaft of the transfer gear.
• the output shaft is permanently connected to a first shaft of the main gearset.
• the transfer gearset comprises, in addition to the first and second shafts, exactly three further shafts, namely a third shaft, a fourth shaft and a fifth shaft.
• the third shaft of the transfer gearset is continuously connected to a second shaft of the main gearset, and connectable by closing a first of the shift elements with the fourth shaft of the transfer gearset.
• the fourth wave of the Vorschaltradsatzes is rotatably determined by closing a second of the switching elements.
• the fifth wave of the transfer gearset can be locked in place by closing a third of the shift elements.
• the speed of one or more of the four countershaft axles may also assume negative values, or even the value zero.
• the speed order is therefore always to refer to the signed value of the speeds, and not on the amount. If two of the four transfer gear set shafts are connected to each other, so have the four Vorschaltradsatzwellen the same speed.
• the inventive kinematics of the transfer gearset, the assignment of the three switching elements to the five Vorschaltradsatzwellen, and the permanent connection of the transfer gearset to a Hauptradsatzwelle, to the drive shaft and the rotor of the electric machine allow the following functions: - Are the first switching element and the third switching element is closed, and the second switching element is opened, the speed of the third Vorschaltradsatz- wave is reduced in comparison to the speed of the drive shaft. The closing of the first and third switching element thus causes the typical for a Vorschaltradsatz speed reduction.
• the rotor of the electric machine turns amount faster than the drive shaft.
• the electrical machine can thus be designed for higher speeds and lower torque with the same power requirement, whereby the space requirement of the electric machine can be reduced.
• This is preferably realized by a magnitude larger choice of the stationary gear ratio of the first planetary gear set as the amount of stationary gearbox ratio of the second planetary gear set.
• the stationary gear ratio defines the speed ratio between the sun gear and ring gear of a planetary gear set with non-rotatable web.
• the stationary gear gear ratio always has a negative value for a negative gear set.
• a minus wheel set denotes a planetary gear set with a web on which the planet gears are rotatably mounted, with a sun gear and with a ring gear, wherein the toothing of at least one of the planetary gears meshes with both the teeth of the sun gear, as well as with the teeth of the ring gear, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates at a fixed web.
• a plus gear set differs from the negative planetary gear set just described in that the plus gear set has inner and outer planet gears rotatably supported on the land. The toothing of the inner planet gears meshes on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planetary gears.
• the toothing of the outer planetary gears also meshes with the teeth of the ring gear. This has the consequence that rotate at a fixed land, the ring gear and the sun gear in the same direction. If a minus wheel set is replaced by a plus wheel set, in addition to the changed connection of the elements bridge and ring gear, the amount of the stationary gear ratio by the value of one to increase to achieve the same translation effect.
• Each of the two planetary gear sets of the transfer gearset has a first, second and third element, which are preferably associated in the following manner the elements sun gear, web and ring gear of the planetary gear sets: the first element is formed by the sun gear of the respective planetary gear set.
• the second element is formed by the web of the respective planetary gear set, and the third element by the ring gear of the respective planetary gear set.
• the second element is formed by the ring gear of each planetary gear set, and the third element through the web of the respective planetary gear set.
• the third element of the second planetary gear set is part of the first wave of the Vorschaltradsatzes.
• the first element of the first planetary gear set and the first element of the second planetary gear set are connected to each other, and components of the second shaft of the transfer gear.
• the third element of the first planetary gear set is part of the third wave of the Vorschaltradsatzes.
• the second element of the second planetary gear set is part of the fourth wave of the transfer gear.
• the second element of the first planetary gear set is part of the fifth wave of the Vorschaltradsatzwelle.
• Such a construction of the transfer gearset has a compact design and a good gear efficiency.
• the main gearset is designed as a planetary gearset system which, in addition to the first and second shaft, comprises exactly two further shafts, namely a third shaft and a fourth shaft. If a planetary gear set system forms four shafts, the planetary gearset system is characterized primarily by its kinematics, not by its structure. The speeds of the four shafts are linearly dependent on each other once the speed of two of the four waves is defined.
• the four shafts of the main gearset have the following speed order: second shaft, third shaft, first shaft, fourth shaft.
• speed order is understood the order of the Weinradsatzwellen in their linear speed dependence.
• the speed of the second main gear set shaft is less than or equal to the speed of the third main gear set shaft.
• the speed of the third main gear set shaft is again less than or equal to the speed of the first main gear set shaft.
• the speed of the first main gear set shaft is less than or equal to the speed of the fourth main gear set shaft.
• This order is also reversible, so that the fourth main gear set shaft has the lowest rotational speed, while the second main gear set shaft assumes a rotational speed which is greater than or equal to the rotational speed of the fourth main gear set shaft.
• the speed of one or more of the four main gearset shafts can also negative values, or assume the value zero.
• the speed order is therefore always to refer to the signed value of the speeds, and not on the amount. If two of the four main gearset shafts are connected together, the four main gearset shafts have the same speed.
• the third wave of the main gearset is rotatably fixable.
• the drive shaft is connectable to the fourth shaft of the main gearset.
• the drive shaft can be connected to the third shaft of the main gearset.
• the planet tenradsatzsystem on a first planetary gear set and a second planetary gear set which each have a first element, a second element and a third element.
• the first element is formed by the sun gear of the respective planetary gear set.
• the second element is formed by the web of the respective planetary gear set, and the third element by the ring gear of the respective planetary gear set.
• the second element is formed by the ring gear of the respective planetary gear set, and the third element through the web of the respective planetary gear set.
• the second element of the second planetary gear set and the third element of the first planetary gear set are connected to each other and are components of the first shaft of the main gearset.
• the first element of the first planetary gear set is part of the second shaft of the main gearset.
• the second element of the first planetary gear set and the third element of the second planetary gear set are components of the third wave of the main gearset.
• the first element of the second planetary gear set is part of the fourth wave of the main gearset.
• the main gearset is formed as a Planetenradsatzsystem, which comprises in addition to the first and second shaft exactly three other waves, namely a third wave, a fourth wave and a fifth wave.
• the fifth wave of the planetary gear set system is constantly connected to the drive shaft.
• the third wave of the Planetenradsatzsystems is rotatably fixable.
• the third shaft of the Planetenradsatzsystems with the fourth shaft of the Planetenradsatzsystems is connectable, so that when the fifth switching element is closed, the waves of the Planetenradsatzsystems have the following speed order: second shaft, third shaft together with fourth shaft, first shaft, fifth shaft.
• the drive shaft is connectable to the third shaft of the Planetenradsatzsystems.
• a shaft of the main gearset with the drive shaft is constantly connected, while the main gearset is similar to the Vorschaltradsatz now constructed as a five-shaft gearbox.
• the second embodiment can simplify the storage of the drive shaft, and shorten the axial length of the transmission.
• the Planetenradsatzsystem two planetary gear sets which each have a first element, a second element and a third element.
• the first element is always formed by the sun gear of the respective planetary gear set.
• the second element is formed by the web of the respective planetary gear set, and the third element by the ring gear of the respective planetary gear set.
• the second element is formed by the ring gear of each planetary gear set, and the third element through the web of the respective planetary gear set.
• the second element of the second planetary gear set and the third element of the first planetary gear set are connected to each other and are components of the first shaft of the main gearset.
• the first element of the first planetary gear set is part of the second wave of the Gearset.
• the second element of the first planetary gear set is part of the third wave of the main gearset.
• the third element of the second planetary gear set is part of the fourth wave of the main gearset.
• the first element of the second planetary gear set is part of the fifth wave of the main gearset.
• a structure according to the first or second embodiment enables the formation of seven forward gears and at least one reverse gear between the drive shaft and the output shaft by selectively closing three of the shift elements.
• a first forward speed results from closing the second, fourth and fifth shift elements. In this case, the ratio between the drive shaft and output shaft is already fixed by closing the fourth and the fifth switching element. By closing the second switching element, the rotational speeds of the remaining waves are fixed, whereby the control of the transmission is simplified.
• a second forward gear is obtained by closing the first, the second and the fifth shift element.
• a third forward speed is achieved by closing the second, the third and the fifth switching element.
• a fourth forward speed is achieved by closing the second, fifth and sixth shifting elements.
• the ratio between the drive shaft and output shaft is already fixed by closing the fifth and the sixth switching element.
• closing the second switching element By closing the second switching element, the rotational speeds of the remaining waves are fixed, whereby the control of the transmission is simplified.
• a fifth forward speed is achieved by closing the second, third and sixth shifting elements.
• a sixth forward speed results from closing the first, third and sixth shift elements.
• a seventh forward gear is obtained by closing the first, second and sixth shifting elements.
• a structure according to the first or second embodiment also allows a power-split operation between the drive shaft, the electric machine and the output shaft.
• the output shaft speed can be changed continuously for a given speed of the drive shaft and specification of the rotor speed.
• a starting operation can be represented without using a separate or integrated starting element for providing a speed compensation between transmission-external drive unit and output shaft.
• a first power-split drive mode is obtained by closing the third switching element and the fifth switching element, this first power-split drive mode being particularly suitable for starting in the forward direction.
• a second power-split drive mode is obtained by closing the fourth switching element and the first switching element, wherein this second power-split drive mode is particularly suitable for starting in the reverse direction.
• a structure according to the first or second embodiment enables further operating modes, which are particularly suitable for use in a hybrid vehicle.
• a drive of the output shaft by means of the electric machine is possible without driving the drive shaft.
• the electric machine can be driven by means of the drive shaft, without driving the output shaft.
• an energy store can be charged by regenerative operation of the electric machine without driving the motor vehicle.
• a power shift between fifth and sixth forward speed can be supported by means of the electric machine, since the thereby remaining closed
• the fourth and / or the second switching element is designed as a positive-locking switching element.
• Positive-locking switching elements make the connection in the closed state by positive locking, and are characterized in the open state by lower drag losses than non-positive switching elements. By low in the open state drag losses the efficiency of the transmission is improved.
• the fourth and / or the second switching element may be formed as a frictionally engaged friction switching element, the lamellae having exclusively coating-free friction surfaces. In other words, the disk-shaped main body of each slat of the
• Reibschaltelements not applied to the blade friction lining.
• the friction surfaces of individual or all lamellae of such a Reibschaltelements can be heat treated, for example, nitrided.
• Such Reibschaltium are designed for high surface pressures, and can therefore be formed with a small friction surface and a few fins. This allows the
• an interface of the transmission to a transmission-external drive unit and an interface of the output shaft to a transmission-internal or transmission-external differential gear are arranged coaxially with each other and at opposite axial ends of the transmission.
• the interface to the transmission-external drive unit is designed to transmit a rotational movement from the transmission-external drive unit to the transmission, and may be formed, for example, as a flange or as a spline.
• the interface may be formed on the drive shaft or on a connectable with the drive shaft connecting shaft.
• the interface may also be formed, for example, on a hydrodynamic torque converter connected to the drive shaft, which serves as a starting element.
• the interface to the differential gear is aligned for transmitting a rotational movement from the output shaft to the drive wheels of the motor vehicle, with the interposition of the differential gear.
• the axial distance between the interface to the transmission-external drive unit and the main gearset is greater than the axial distance between the interface to the transmission-external drive unit and the Vorschaltrad- sentence.
• the interface of the output shaft is formed as a spur gear, which meshes with a further spur gear toothing of a shaft parallel to the axis of rotation to the output shaft.
• the interface of the output shaft has a shorter axial distance to the interface of the drive shaft than the Vorschaltradsatz.
• the main gearset is preferably arranged axially between the spur gear teeth of the output shaft and the transfer gearset.
• the transfer gearset is in such an arrangement at that axial end of the transmission, which is opposite to the interface to the transmission-external drive unit.
• the transmission may have a connection shaft, which serves as an interface to a gear-external drive unit, for example an internal combustion engine.
• the connecting shaft can be connected to the drive shaft via a separating clutch.
• the separating clutch together with the connecting shaft can also be arranged outside of the transmission.
• the separating clutch may be formed as a positive or non-positive switching element.
• the transmission may comprise a torsional vibration damper, which is adapted for damping torsional vibrations, and is preferably arranged in the operative connection between two sections of the connecting shaft.
• the first section of the connection shaft is assigned to the interface to the transmission-external drive unit, and the second section of the connection shaft is assigned to the separation clutch.
• a starting element for example a hydrodynamic torque converter or a friction clutch.
• Such a starting element can also be an integral part of the transmission.
• the starting element allows when using the transmission in the motor vehicle powertrain a starting process by allowing a slip state between the engine and output shaft.
• such a starting element is formed within the transmission by the fourth switching element is designed as a friction switching element.
• the fourth switching element By slip operation of the fourth switching element, a starting operation in the first forward gear and in reverse is possible. Thus, a separate starting element can be omitted. If the fourth shift element is designed as a form-locking shift element or does not permit precise control of a slip state, then a slip state can be achieved during start-up by the fifth shift element for a start-up operation in the forward direction and by the third shift element for a start-up operation in the reverse direction, the third and fifth Switching element are to train as suitable non-positive switching elements.
• the transmission may be part of a drive train of a motor vehicle.
• the drive train also has an internal combustion engine, which is torsionally flexible connected or connectable to the drive shaft of the transmission via a torsional vibration damper. Between drive shaft and internal combustion engine, the separating clutch may be located, which may be part of the transmission.
• the output shaft of the transmission is drivirkswunden with a differential gear, which is operatively connected to wheels of the motor vehicle. If the transmission has the electric machine, the drive train enables a plurality of drive modes of the motor vehicle. In an electric driving operation, the motor vehicle is driven by the electric machine of the transmission. In an internal combustion engine operation, the motor vehicle is driven by the internal combustion engine.
• a permanent connection is called a connection between two elements that always exists. Such constantly connected elements always rotate with the same dependence between their speeds. In a permanent connection between two elements, no switching element can be located. A permanent connection must therefore be distinguished from a switchable connection.
• a permanently non-rotatable connection is referred to as a connection between two elements, which always exists and their connected elements thus always have the same speed.
• closing of a switching element in the context of gear formation is understood to mean a process in which the switching element is activated in such a way that it transmits a high degree of torque at the end of the closing operation is in non-positive switching elements in the "closed” state, the formation of a low differential speed between the switching element halves wanted or unintentionally possible.
• Fig. 1 is an abstract representation of a transmission according to the invention
• Fig. 2 is a schematic representation of a transmission according to a first embodiment of the invention
• FIG. 3 is a speed diagram of the main gearset according to the first embodiment
• Fig. 5 is a schematic representation of a transmission according to a second embodiment of the invention.
• Fig. 6 is a circuit diagram of the transmission according to the second embodiment
• Fig. 7 is a schematic representation of a transmission according to a third embodiment of the invention
• Fig. 8 is a circuit diagram of the transmission according to the third embodiment
• Fig. 9 is a schematic representation of a transmission according to a fourth embodiment of the invention.
• Fig. 1 a drive train of a motor vehicle.
• Fig. 1 shows an abstract representation of a transmission G according to the invention.
• the transmission G has a drive shaft GW1, an output shaft GW2, an electric machine EM with a rotationally fixed stator S and a rotatable rotor R, a transfer gearset VRS and a main gearset HRS.
• the structure of the Vorschal- tradsatzes VRS is exemplified, while the structure of the main gearset HRS is only hinted at.
• the main gearset HRS has several shafts, including a first shaft Wy1, which is permanently connected to the drive shaft GW2, and a second shaft Wy2.
• the transfer gearset VRS has five shafts, which are referred to as first shaft Wx1, second shaft Wx2, third shaft Wx3, fourth shaft Wx4 and fifth shaft Wx5.
• the five shafts Wx1 to Wx5 of the transfer gearset VRS are formed by the elements of a first planetary gear set P1 and a second planetary gear set P2.
• Each of the two planetary gear sets P1, P2 has a first element E1 1, E12, a second element E21, E22 and a third element E31, E32.
• the first element E1 1, E12 is formed by a sun gear of the respective planetary gear set P1, P2.
• the second element E21, E22 is formed by a web of the respective planetary gear set P1, P2 and the third element E31, E32 by the ring gear of the respective planetary gear set P1, P2.
• the planetary gear sets P1, P2 are designed as minus wheelsets.
• the third element E32 of the second planetary gear set P2 is part of the first wave Wx1 of the transfer gearset VRS, and is permanently connected to the drive shaft GW1.
• the first element E1 1 of the first planetary gear P1 and the first Element E12 of the second planetary gearset P2 are constantly connected to each other and components of the second wave Wx2 of the transfer gearset VRS, which is permanently connected to the rotor R of the electric machine EM.
• the third element E31 of the first planetary gear set P1 is part of the third wave Wx3 of the transfer gearset VRS, which is permanently connected to the second shaft Wy2 of the main gearset HRS.
• the second element E22 of the second planetary gear set P2 is part of the fourth wave Wx4 of the transfer gearset VRS.
• the second element E21 of the first planetary gear set P1 is part of the fifth wave Wx5 of the transfer gearset VRS.
• the transmission G has a plurality of switching elements, including a first switching element 57, a second switching element 07 and a third switching element 08.
• the first switching element 57 By closing the first switching element 57, the third Vorschaltradsatzwelle Wx3 is connected to the fourth Vorschaltradsatzwelle Wx4.
• the second switching element 07 By closing the second switching element 07, the fourth Vorschaltradsatzwelle Wx4 is fixed in rotation by being connected to a non-rotatable component GG of the transmission G.
• the rotationally fixed component may be formed, for example, by the housing of the transmission G.
• the third switching element 08 By closing the third switching element 08, the fifth wave Wx5 of the transfer gearset VRS is rotatably fixed in the same way.
• the main gearset HRS can be constructed in various ways.
• the main gearset HRS may have only a single planetary gear set or a plurality of planetary gear sets.
• the main gearset could also be constructed as a countershaft transmission.
• the main gearset HRS can be assigned switching elements with which individual shafts of the main gearset HRS can be fixed against rotation or connected to the drive shaft GW1. By means of the switching elements, individual shafts of the main gearset HRS can also be interconnected. Concrete embodiments of gears G are described in detail in the following embodiments.
• the drive shaft GW1 has an interface A to a drive-external drive unit.
• the output shaft has an interface B to a gear external or internal transmission differential gear.
• the interfaces A, B are coaxial xial to each other and arranged at opposite axial ends of the transmission G.
• the interface A is designed to transmit a rotational movement from the transmission-external drive unit to the gear G, and may be formed, for example, as a flange or as a spline.
• the interface A may be formed on the drive shaft GW1 or on a connectable with the drive shaft GW1 connection shaft.
• the interface A can also be formed, for example, on a hydrodynamic torque converter connected to the drive shaft GW1, which serves as a starting element.
• the interface B of the output shaft GW2 is aligned to transmit a rotational movement of the output shaft GW2 to drive wheels of the motor vehicle, with the interposition of the differential gear.
• Fig. 2 shows a schematic representation of a transmission G according to a first embodiment of the invention.
• the main gearset HRS has a planetary gearset system PS1, which comprises a first planetary gearset P3 and a second planetary gearset P4.
• Each of the two planetary gear sets P3, P4 has a first element E13, E14, a second element E23, E24 and a third element E33, E34.
• the first element E13, E14 is formed by a sun gear of the respective planetary gear set P3, P4.
• the second element E23, E24 is formed by a web of the respective planetary gear set P3, P4 and the third element E33, E34 by the ring gear of the respective planetary gear set P3, P4.
• the planetary gear sets P3, P4 are designed as minus wheelsets.
• the planetary gearset PS1 has exactly four waves, namely the first shaft Wy1 connected to the output shaft GW2, the second shaft Wy2 connected to the third shaft Wx3 of the transfer gearset VRS, a third shaft Wy3 and a fourth shaft Wy4.
• a Planetenradsatzsystem consisting of two individual Planetenrad algorithmsn, which together form four waves can also be described by its kinematics. Examples include the so-called Ravigneaux wheelset or the Simpson wheelset.
• the four shafts of such planetary gear set systems Have a speed order, which will be described in detail hereinafter with reference to FIG. 3 in detail.
• the first shaft Wy1 of the main gearset HRS is permanently connected to the third element E33 of the first planetary gearset P3 and to the second element E24 of the second planetary gearset P4.
• the second wave Wy2 of the main gearset HRS is permanently connected to the first element E13 of the first planetary gearset P3.
• the third wave Wy3 of the main gearset HRS is continuously connected to the second element E23 of the first planetary gear set P3 and to the third element E34 of the second planetary gear set P4.
• the third wave Wy3 of the main gearset HRS can be fixed in a rotationally fixed manner by closing a fourth switching element 04.
• the fourth wave Wy4 of the main gearset HRS is continuously connected to the first element E14 of the second planetary gear set P4, and connectable via a fifth switching element 13 to the drive shaft GW1.
• the third wave Wy3 of the main gearset HRS is connectable by closing a sixth switching element 14 with the drive shaft GW1.
• the transmission G according to the first embodiment shown in Fig. 1 has a connection shaft AN, which is connectable via a separating clutch K0 with the drive shaft GW1. These two components are optional components of the transmission G.
• the interface A is formed on the connection shaft AN.
• FIG. 3 shows a speed plan of the planetary gearset system PS1 according to the transmission G of the first embodiment shown in FIG.
• the four vertical lines describe the rotational speed of each of the four main gear set shafts Wy1 to Wy4 in relation to a predetermined rotational speed n of the drive shaft GW1, which is normalized to the value one.
• the distance between the vertical lines results from the stationary gear ratios of the planetary gear sets P3, P4.
• the representation shown in Fig. 3 is not to scale.
• Circles arranged on the vertical lines indicate the effect of the six switching elements 57, 07, 08, 04, 13, 14. If, for example, the drive shaft GW1 is connected to the fourth shaft Wy4 by closing the fifth shift element 13, then For example, the fourth shaft Wy4 and the drive shaft GW1 are at a speed ratio equal to one. If the fourth switching element 04 is closed, the rotational speed of the third shaft Wy3 is equal to zero.
• the three shift elements 57, 07, 08 assigned to the transfer gearset VRS have their effect by closing two of the three shift elements 57, 07, 08. If the first shift element 57 and the second shift element 07 are closed, then the second shaft W2y is fixed against rotation, and therefore assumes the value zero.
• the rotational speed of the second shaft W2y is reduced in relation to the rotational speed n of the drive shaft GW1. If the second shift element 07 and the third shift element 08 are closed, the rotational speed of the second shaft W2y is likewise reduced in relation to the rotational speed n of the drive shaft GW1, but to a lesser extent than when the first and third shift elements 57, 08 are closed.
• the rotational speeds of all four waves Wy1 to Wy4 of the main gearset HRS are set. This can be seen by straightforward connection of two of the circles.
• the rotational speeds of the four waves Wy1 to Wy4 are therefore linearly dependent on one another as soon as the rotational speed of two of the four waves Wy1 to Wy4 is defined.
• the order of the vertical lines in the speed diagram indicates the speed order, which in the given example assumes the following sequence: second wave Wy2, third wave Wy3, first wave Wy1, fourth wave Wy4.
• Fig. 4 shows a circuit diagram which is applicable to the transmission G according to the first embodiment.
• two reverse gears R1, R2 and a first to seventh forward gear 1 to 7 are indicated.
• the columns of the circuit diagram is marked by an X, which of the switching elements 04, 07, 08, 13, 14, 57 in which gear 1 to 7 or R1, R2 are closed.
• the gears refer to fixed gear ratios between the drive shaft GW1 and the output shaft GW2.
• a first forward gear 1 is obtained by closing the fourth and the fifth shifting element 04, 13.
• a second forward gear 2 is obtained by closing the first, the second and the fifth shift element 57, 07, 13.
• a third forward gear 3 is obtained by closing the second, the third and the fifth shift element 07, 08, 13.
• a fourth forward gear 4th is obtained by closing the fifth and the sixth switching element 13, 14.
• a fifth forward gear 5 is obtained by closing the second, the third and the sixth shift element 07, 08, 14.
• a sixth forward gear 6 is obtained by closing the first, the third and the sixth shift element 57, 08, 14.
• a seventh forward gear. 7 is obtained by closing the first, the second and the sixth switching element 57, 07, 14.
• a designated as R1 first reverse gear is obtained by closing the first, third and fourth switching element 57, 08, 04.
• a second reverse gear R2 can by closing the second, the third and the fourth switching element 07, 08, 04 are formed.
• a first power-split drive mode EDA1 is obtained by closing the third and the fifth shift element 08, 13.
• a second power split drive mode EDA2 is obtained by closing the first and the fourth shift element 57, 04.
• An electric drive mode E1 results from closing the third and fifth drive elements fourth switching element 08, 04.
• Fig. 5 shows a schematic representation of a transmission G according to a second embodiment of the invention.
• the main gearset HRS has a planetary gearset system PS2, which comprises a first planetary gearset P23 and a second planetary gearset P24.
• Each of the two planetary gear sets P23, P24 has a first element E213, E214, a second element E223, E224 and a third element E233, E234.
• the first element E213, E214 is formed by a sun gear of the respective planetary gear set P23, P24.
• the second element E223, E224 is formed by a web of the respective planetary gear set P23, P24 and the third element E233, E234 by the ring gear of the respective planetary gear set P23, P24.
• the planetary gear sets P23, P24 are designed as minus wheelsets.
• the planetary gear set PS2 has exactly five waves, namely the first shaft Wy21 connected to the output shaft GW2, the second shaft Wy22 connected to the third shaft Wx3 of the transfer gearset VRS, a third shaft Wy23, a fourth shaft Wy24 and a fifth shaft Wy25.
• the first shaft Wy21 of the main gearset HRS is permanently connected to the third element E233 of the first planetary gearset P23 and to the second element E224 of the second planetary gearset P24.
• the second shaft Wy22 of the main gearset HRS is permanently connected to the first element E213 of the first planetary gear set P23.
• the third wave Wy23 of the main gearset HRS is continuously connected to the second element E223 of the first planetary gearset P3.
• the third wave Wy23 of the main gearset HRS by rotation of a fourth switching element 204 can be fixed in rotation.
• the fourth wave Wy24 of the main gearset HRS is continuously connected to the third element E34 of the second planetary gearset P4.
• the fifth shaft Wy25 of the main gearset HRS is continuously connected to the first element E214 of the second planetary gear set P4, and continuously connected to the drive shaft GW1.
• the third shaft Wy23 of the main gearset HRS is connectable by closing a fifth shift element 234 to the fourth shaft Wy24 of the main gearset HRS, and by closing a sixth shift element 214 to the drive shaft GW1.
• the difference between the first and second embodiments is therefore essentially the coupling between the first element E14, E214 of the second planetary gear set P4, P24 and the drive shaft GW1 on the one hand, and the coupling between the second element E23, E223 of the first planetary gear P3, P23 and the third element E34, E234 of the second planetary gear set P4, P24 on the other hand.
• One of the two couplings is designed as a permanently rotationally fixed connection, while the other of the two couplings is designed as a switchable by means of the fifth switching element 13, 234 connection.
• Fig. 6 shows a circuit diagram which is applicable to the transmission G according to the second embodiment.
• Fig. 7 shows a schematic representation of a transmission G according to a third embodiment of the invention.
• the main gearset HRS in this case has a single planetary gear set P33, which has a first element E313, a second element E323 and a third element E333.
• the first element E313 is formed by a sun gear of the planetary gear set P33.
• the second element E323 is formed by a web of the planetary gear set P33 and the third element E333 by a ring gear of the planetary gear set P33.
• the second element E323 would be formed by the ring gear of the planetary gear set P33 and the second element E333 through the web of the planetary gear P33.
• the main gearset HRS has exactly three waves, namely the first shaft Wy31 connected to the output shaft GW2, the second shaft Wy32 connected to the third shaft Wx3 of the transfer gearset VRS, and a third shaft Wy33.
• the second element E323 of the planetary gear set P33 is part of the first wave Wy31 of the main gearset HRS.
• the third element E333 of the planetary gear set P33 is part of the second wave Wy32 of the main gearset HRS.
• the first element E313 of the planetary gear set P33 is part of the third wave Wy33 of the main gearset HRS.
• the drive shaft GW1 can be connected to the third shaft Wy33.
• the interface B is formed in the gear G according to the third embodiment as a spur gear, which meshes with a further spur gear toothing of an output shaft parallel to the axis, not shown in Fig. 7 shaft.
• the main gearset HRS is arranged axially between the interface B and the ballast VRS.
• the interface B is arranged axially between the interface A to the transmission-external drive unit and the transfer gear VRS.
• Fig. 8 shows a circuit diagram which is applicable to the transmission G according to the third embodiment.
• a first to fifth forward gear 21 to 25 are indicated.
• an X which of the switching elements 304, 07, 08, 234, 314, 57 in which gear 21 to 25 are closed.
• the gears refer to fixed gear ratios between the drive shaft GW1 and the output shaft GW2.
• Fig. 9 shows a schematic representation of a transmission G according to a fourth embodiment of the invention.
• the main gearset HRS has a planetary gearset system PS3, which comprises a first planetary gearset P43 and a second planetary gearset P44.
• Each of the two planetary gear sets P43, P44 has a first element E413, E414, a second element E423, E424 and a third element E433, E434.
• the first element E413, E414 is formed by a sun gear of the respective planetary gear set P23, P24.
• the second element E423, E424 is formed by a web of the respective planetary gear set P43, P44 and the third element E433, E434 by a ring gear of the respective planetary gear set P33, P34. If one of the planetary gear sets P43, P44 is designed as a plus-wheel set, then the second element E423, E424 is formed by the ring gear of the respective planetary gear set P43, P44, and the third element E433, E434 by the web of the respective planetary gear set P33, P34.
• the first planetary gear set P43 is designed as a plus-wheel set, and the second planetary gear set P44 as a minus-wheel set.
• the planetary gear set PS4 has exactly four waves, namely the output shaft connected to the output shaft GW2 Wy41, the second wave Wy42, a third wave Wy3 and a fourth wave Wy4 connected to the third wave Wx3 of the VRS.
• a Planetenradsatzsystem consisting of two individual Planetenrad accountsn, which together form four waves can also be described by its kinematics.
• the present structure of the planetary gear set corresponds to the well-known Ravigneaux wheelset.
• the embodiment shown in Fig. 9 is to be considered only schematically.
• the main gearset HRS would be constructed in the known construction a Ravigneaux wheelset, ie with a single ring gear and a common set of radially outer planetary gears.
• the second element E423 of the first planetary gear set P43 and the third element R434 of the second planetary gear set P44 are components of the first shaft Wy41 of the main gearset HRS, which is permanently connected to the output shaft GW2.
• the first element E413 of the first planetary gear set P43 is part of the second wave Wy42 of the main gearset HRS; which is permanently connected to the third wave Wx3 of the VRS.
• the third element E433 of the first planetary gear set P43 and the second element E424 of the second planetary gear set P44 are components of the third wave Wy43 of the main gearset HRS.
• the first element E414 of the second planetary gear set P44 is part of the fourth wave Wy44 of the main gearset HRS.
• the third wave Wy43 can be locked in place by closing a fourth switching element 403.
• the fourth shaft Wy44 is connectable to the drive shaft GW1 by closing a fifth shift element 414, and to the second shaft Wy42 by closing a sixth shift element 445.
• Fig. 10 shows a circuit diagram which is applicable to the transmission G according to the fourth embodiment.
• a reverse gear 3R and a first to eighth forward gear 31 to 38 are indicated.
• an X which of the switching elements 403, 07, 08, 414, 445, 57 in which gear 31 to 38, 3R are closed.
• the gears refer to fixed gear ratios between the drive shaft GW1 and the output shaft GW2.
• Fig. 1 1 shows schematically a drive train of a motor vehicle.
• An internal combustion engine VKM is connected to the connection shaft AN of the transmission G via a torsional vibration damper TS.
• the transmission G shown in Fig. 1 corresponds to the first embodiment of the invention shown in Fig. 1. This is only an example.
• the internal combustion engine VKM could also be connected directly to the drive shaft GW1 of the transmission G via the torsional vibration damper TS.
• the powertrain could be implemented with any of the subject embodiments.
• the powertrain could also include a hydrodynamic torque converter, which is to be arranged in the power flow between the internal combustion engine VKM and the drive shaft GW1 of the transmission G. Such a torque converter may also include a lock-up clutch.
• the output shaft GW2 is connected to a differential gear AG, via which the power applied to the output shaft GW2 power is distributed to drive wheels DW of the motor vehicle.

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• 2016
  • 2016-05-19 DE DE102016208669.3A patent/DE102016208669A1/de not_active Withdrawn
• 2017
  • 2017-04-27 EP EP17720117.5A patent/EP3458295A1/de not_active Withdrawn
  • 2017-04-27 KR KR1020187036458A patent/KR20190010599A/ko not_active Application Discontinuation
  • 2017-04-27 US US16/302,868 patent/US20190291564A1/en not_active Abandoned
  • 2017-04-27 CN CN201780030419.3A patent/CN109153325A/zh active Pending
  • 2017-04-27 WO PCT/EP2017/060106 patent/WO2017198442A1/de unknown
  • 2017-04-27 JP JP2018560638A patent/JP2019522153A/ja not_active Withdrawn

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