[go: up one dir, main page]

WO2015082168A1 - Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique - Google Patents

Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique Download PDF

Info

Publication number
WO2015082168A1
WO2015082168A1 PCT/EP2014/073881 EP2014073881W WO2015082168A1 WO 2015082168 A1 WO2015082168 A1 WO 2015082168A1 EP 2014073881 W EP2014073881 W EP 2014073881W WO 2015082168 A1 WO2015082168 A1 WO 2015082168A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear set
hrs
planetary gear
main gearset
transmission
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2014/073881
Other languages
German (de)
English (en)
Inventor
Peter Ziemer
Andreas Beisswenger
Christian Sibla
Raffael Kuberczyk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of WO2015082168A1 publication Critical patent/WO2015082168A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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 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 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
    • 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 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 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 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 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
    • 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 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—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 externally powered electric machines
    • F16H3/725—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 externally powered electric machines with means to change ratio in the mechanical gearing
    • 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
    • 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 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 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4816—Electric machine connected or connectable to gearbox internal shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2025—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 5 connections
    • 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
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four 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
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • 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 having a transmission input shaft and a transmission output shaft, a main gearset, a 1925radsatz, and an electric machine having a rotor and a stator, wherein the transmission has at least one power path between the transmission input shaft and the main gear, wherein the main gearset having a first and a second planetary gear set with a total of four in speed order as the first, second, third and fourth waves, the at least one power path via at least one switching element with at least one of the four shafts of the main gear is connectable, wherein the third shaft the main gearset is connected to the transmission output shaft, and wherein the auxiliary gearset includes a planetary gear set having first, second and third shafts, the first shaft of the auxiliary gearset being connected to the rotor.
  • the invention also relates to a drive train for a motor vehicle with a transmission.
  • 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 capability of the drive unit to the driving resistance of the vehicle in a suitable manner.
  • the transmission includes at least a transmission input shaft and a transmission output shaft, a main gearset, a 1925radsatz, and an electric machine with a rotor and a stator.
  • the main gearset has a first and a second planetary gear set with a total of four designated in speed order as the first, second, third and fourth wave waves.
  • the main gearset is thus designed as a two-bar four-shaft gearbox.
  • the relieveradsatz has a planetary gear set with a total of three designated as first, second, and third wave waves.
  • the first shaft of soirradsatzes is permanently connected to the rotor.
  • a coupling shaft is defined as a permanent mechanical connection between an element - ie sun gear or web or ring gear - of the first single planetary gear set with one element - ie sun gear or web or ring gear - of the second single planetary gear set
  • the number of free shafts is defined not by the visual appearance of the transmission, but by its kinematics: In each of the gears of a two-bridge four-shaft transmission, two of the shifting elements connected to elements of the two-bridge four-shaft transmission must be used The graphical representation of the kinematics of the transmission is usually a speed plan of the transmission used, for example, the known from the Gauge Kutzbach plan.
  • Known embodiments for a sol- Two-bridge four-shaft gearboxes are the so-called Ravigneaux wheelset and the so-called Simpson wheelset.
  • a reduced two-bridge four-shaft transmission is a design of a two-bridge four-shaft transmission, in which an element - ie a sun gear, a bridge or a ring gear - of the transmission is saved, as another element of the Getriebes takes over its task without changing the kinematics thereby.
  • the element which takes over the function of the saved element is thus at the same time one of the coupling shafts of the transmission.
  • a known embodiment of this is the Ravigneaux wheelset, which has either two sun gears and only one ring gear or two ring gears and only one sun gear.
  • the transmission input shaft via at least one switching element with at least one of the four shafts of the main gear is connectable.
  • the at least one power path can be connected via two switching elements to two of the four shafts of the main gearset. By closing one of the switching elements thus a rotationally fixed connection between the at least one power path and one of the four shafts of the main gear is made, whereby torque from the transmission input shaft to the main gear is feasible.
  • at least one power path is meant that the transmission has one or more power paths between the transmission input shaft and the main gearset.
  • the third wave of the main gearset is connected to the transmission output shaft.
  • the transmission input shaft When used in a motor vehicle, the transmission input shaft is connected to a shaft of a drive unit or connectable via a coupling, so that mechanical power of the drive unit of the transmission input shaft can be fed.
  • the drive unit can be designed both as an internal combustion engine and as an electrical machine.
  • the transmission output shaft serves as
  • a shaft is not to be understood below exclusively as an example cylindrical, rotatably mounted machine element for transmitting torque, but these are also general fasteners to understand that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotatably together.
  • a planetary gear set includes a sun gear, a land and a ring gear. Rotatably mounted on the web are planet gears, which mesh with the toothing of the sun gear and / or with the toothing of the ring gear.
  • a negative gearset describes a planetary gear set with a web on which the planetary gears are rotatably mounted, with a sun gear and with a ring gear, wherein the toothing meshes with at least one of the planet gears both with the toothing of the sun gear and with the toothing 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 stationary web.
  • Both sun gear and ring gear of a planetary gear set can also be divided into several segments.
  • the planet gears mesh with two sun gears, which are not connected to each other.
  • the speed ratios are of course identical on both segments of the sun gear, as if they were connected together.
  • 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.
  • the stationary gear ratio defines the speed ratio between the sun gear and ring gear of a planetary gear set with non-rotatable web. Since the direction of rotation between the sun gear and the ring gear reverses in the case of a negative gearset when the web is non-rotatable, the stationary gear ratio always assumes a negative value for a negative gearset.
  • the speed diagram shows the speed ratios of the individual shafts in the vertical direction.
  • the horizontal distances between the waves result from the ratios between the waves, so that can be connected to a specific operating point speed ratios and torque ratios of the waves by a straight line.
  • the transmission ratios between the shafts result from the stationary gear ratios of the planetary gear sets involved.
  • the speed plan can be displayed, for example, in the form of a utility plan.
  • first, second, third and fourth wave in the order of rotation are characterized in that the rotational speeds of these waves increase, decrease or become linear in the stated order.
  • the rotational speed of the first shaft is less than or equal to the rotational speed of the second shaft.
  • the speed of the second shaft is again less than or equal to the speed of the third shaft.
  • the speed of the third shaft is less than or equal to the speed of the fourth shaft.
  • This order is also reversible, so that the fourth shaft has the highest speed, while the first shaft assumes a speed which is less than or equal to the speed of the fourth shaft. There is always a linear relationship between the speeds of all four shafts.
  • the speed of one or more waves can 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.
  • the speeds of the four shafts are then the same if two of these elements are connected to each other by the elements ring gear, web and sun of one of the planetary gear sets.
  • switching elements depending on the operating state, a relative movement between two components allowed or made a connection for transmitting a torque between the two components.
  • a relative movement for example, to understand a rotation of two components, wherein the rotational speed of the first component and the rotational speed of the second component differ from each other.
  • the rotation of only one of the two components is conceivable while the other component is stationary or rotating in the opposite direction.
  • the switching elements are preferably designed in the present invention as claw switching elements, which produce the connection by positive locking.
  • Two elements are referred to as being connected to one another, in particular, if a solid, in particular non-rotatable connection exists between the elements. Such connected elements rotate at the same speed.
  • the various components and elements of said invention can be connected to one another via a shaft or via a closed switching element or a connecting element, but also directly, for example by means of a welding, pressing or other connection.
  • Two elements are hereinafter referred to as connectable if there is a releasable rotationally fixed connection between these elements. If the connection is made, such elements rotate at the same speed.
  • An electric machine consists at least of a non-rotatable stator and a rotatably mounted rotor and is configured in a motor operation to convert electrical energy into mechanical energy in the form of speed and torque, and in a regenerative operation mechanical energy into electrical energy in the form of To transform electricity and voltage.
  • the first planetary gearset of the main gearset is designed as a plus gearset
  • the second planetary gearset of the main gearset is designed as a minus gearset.
  • a bridge of the first planetary gear set of the main gearset, a bridge of the second planetary gear set of the main gear and a bridge the planetary gear set of soirradsatzes are interconnected.
  • a ring gear of the planetary gear set of soirradsatzes and a ring gear of the first planetary gear set of the main gearset are interconnected.
  • a sun gear of the planetary gear set of relieveradsatzes meshes with outer planetary gears of the first planetary gear set of the main gearset.
  • the first and second planetary gear set of the main gearset and the planetary gear set of the amidradsatzes are arranged in a first gear set plane and in a second set of wheels.
  • the arrangement of these three planetary gear sets in a total of two wheelset levels of space requirements of the transmission is easily reduced.
  • a Radsatzebene is understood in this context, a plane in which the elements ring gear, land and sun gear of one or more planetary gear sets are arranged. The elements need not be arranged mirror-symmetrically along this plane.
  • the term Radsatzebene is rather interpreted as a space level through which the location of one or more planetary gear sets is characterized in the transmission.
  • the ring gear, web and sun gear of the planetary gear set of Rajradsatzes, and the ring gear and a first portion of the web of the first planetary gear set of the main gearset in the first Radsatz- plane are arranged.
  • a sun gear, the land and a ring gear of the second planetary gear set of the main gearset, and a sun gear and a second portion of the web of the first planetary gear set of the main gearset are arranged in the second wheel set plane.
  • the ring gear of the planetary gear set of relieveradsatzes and the ring gear of the first planetary gear set of the main gearset may be formed as a common ring gear.
  • This common ring gear preferably has a uniform effective diameter.
  • the common ring gear is preferably made in one piece.
  • the sun gear of the first planetary gear set and the sun gear of the second planetary gear set of the main gearset may be embodied as a common sun gear.
  • This common sun gear preferably has a uniform effective diameter.
  • the common sun gear is preferably made in one piece.
  • Such a configuration of the common sun gear and / or ring gear further increases the integration depth of the transmission, and thus contributes to a reduction of the transmission. In addition, this reduces the complexity of the transmission. This simplifies the manufacture and assembly of the transmission.
  • the ring gear of the planetary gear set of Rajradsatzes and the ring gear of the first planetary gear set of the main gear are components of the third wave of beauradsatzes and the third wave of the main gearset.
  • the web of the first planetary gear set and the bridge of the second planetary gear set of the main gear and the web of the planetary gear set of whradsatzes are components of the second shaft of the sansradsatzes and the second wave of the main gearset.
  • the ring gear of the second planetary gear set of the main gearset is part of the first wave of the main gearset.
  • the sun gear of the first planetary gear set and the sun gear of the second planetary gear set of the main gearset are components of the fourth wave of the main gearset.
  • the speed order of the shafts is determined.
  • the first shaft of the beautues is in the speed diagram between the first and second shaft of the main gearset, or the first wave of the main gearset is in the speed diagram between the first shaft of the Rajradsatzes and the second shaft of the main gearset.
  • the rotor is able to assume a rotational speed. This is a prerequisite for receiving and delivering mechanical power by the electric machine.
  • the electric machine makes it possible for the electric machine to be able to absorb or dispense mechanical power even in those gears in which the first shaft of the main gearset is fixed in a rotationally fixed manner or has no appreciable rotational speed.
  • This is particularly advantageous when using the transmission in a motor vehicle, since kinetic energy of the motor vehicle can be recuperated by the regenerative operation of the electric machine in each gear of the transmission. If an internal combustion engine is connected to the transmission input shaft, then the load point of the internal combustion engine can also be shifted by regenerative or motorized operation of the electric machine in each gear.
  • the transmission thus enables an increase in efficiency of the motor vehicle.
  • the transmission has a high functionality despite the low space requirement.
  • Such a transfer gearset may be formed from at least one planetary gear set.
  • the transmission may preferably be part of a hybrid drive train of a motor vehicle.
  • the hybrid powertrain also has an internal combustion engine in addition to the transmission.
  • the internal combustion engine is either directly or via a clutch connected to the transmission input shaft of the transmission, or connectable.
  • the motor vehicle can be driven both by the internal combustion engine and by the electric machine of the transmission.
  • the transmission has an additional electric machine to do so is set up via its rotor to deliver a torque to the transmission input shaft and so to start the internal combustion engine. This has the advantage that the internal combustion engine can be started by means of the additional electric machine, without having to influence a simultaneous electric driving operation, in which the motor vehicle is driven solely by the electric machine of the transmission.
  • the electric machine is connected to a converter, via which the electric machine is connected to an energy store.
  • an energy store for this purpose, any form of energy storage is suitable, in particular electrochemical, electrostatic, hydraulic and mechanical energy storage.
  • the transmission may also be part of a drive train of an electric vehicle.
  • An electric vehicle is driven solely by one or more electric machines, and accordingly has no internal combustion engine.
  • a traction electric machine is connected. Due to the different gear ratios of the transmission, the traction electric machine can always be operated in an operating range with high efficiency, whereby the energy efficiency of the entire electric vehicle is improved.
  • Fig. 1 shows schematically a transmission according to a first embodiment of the invention.
  • Fig. 2 shows a speed diagram of the transmission according to the first embodiment.
  • Fig. 3 shows a circuit diagram of the transmission according to the first embodiment.
  • Fig. 4 shows schematically a transmission according to a second embodiment of the invention.
  • Fig. 5 shows a speed diagram of the transmission according to the second embodiment.
  • Fig. 6 shows a circuit diagram of the transmission according to the second embodiment.
  • Fig. 7 shows a hybrid powertrain of a motor vehicle.
  • Fig. 1 shows schematically a transmission G according to a first embodiment of the invention.
  • the transmission G has an additional gearset ZRS and a main gearset HRS.
  • the additional gear set ZRS has a planetary gear set P4, while the main gearset HRS has a first planetary gear set P1 and a second planetary gear set P2.
  • the first planetary gear set P1 of the main gearset HRS is designed as a plus-wheel set.
  • the second planetary gearset P2 of the main gearset HRS and the planetary gearset P4 of the additional gearset ZRS are designed as minus wheelsets.
  • the representation of the transmission G essentially shows the connectable and connected elements of the transmission G.
  • the distances selected in the representation of the transmission G can not be used to deduce the transmission ratios.
  • a first wave W1 of the main gearset HRS is connected to a ring gear Ho-P2 of the second planetary gearset P2 of the main gearset HRS.
  • a second Shaft W2 of the main gearset HRS is connected to a web St-P1 of the first planetary gearset P1 and to a web St-P2 of the second planetary gearset P2 of the main gearset HRS.
  • a third wave W3 of the main gearset HRS is connected to a ring gear Ho-P1 of the first planetary gearset P1 of the main gearset HRS.
  • a fourth wave W4 of the main gearset HRS is connected to a sun So-P1 of the first planetary gear P1 and with a sun So-P2 of the second planetary gear set P2 of the main gearset HRS.
  • the arrangement of the first, second, third and fourth wave W1, W2, W3, W4 of the main gearset HRS is determined in the speed plan, the order first , second, third, fourth wave W1, W2, W3, W4 whose order corresponds to the speed plan.
  • the third wave W3 of the main gearset HRS is connected to the transmission output shaft GW2.
  • the third wave W3 of the main gearset HRS may also be connected via an additional transmission gear to the transmission output shaft GW2.
  • the first planetary gearset P1 and the second planetary gearset P2 of the main gearset HRS and the planetary gearset P4 are arranged in a first Radsatzebene RSE-1 and in a second Radsatzebene RSE-2.
  • a ring gear Ho-P4 of the planetary gearset P4 of repayradsatzes ZRS, the ring gear Ho-P1 of the first planetary gear P1 of the HRS, a sun So-P4 of the planetary gear P4 of aggrradsatzes ZRS, a bridge St-P4 of the planetary gear P4 of aggrradsatzes ZRS and a first section St-P1 -1 of the web St-P1 of the first planetary gear set P1 of the main gearset HRS are arranged in the first Radsatzebene RSE-1.
  • the sun gear So-P1 of the first planetary gear set P1 of the main gearset HRS, a second section St- P 1 -2 of the web St-P1 of the first planetary gear set P1 of the main gearset HRS, the sun So-P2 of the second planetary gear set P2 of the main gearset HRS, the bridge St-P2 of the second planetary gearset P2 of the main gearset HRS and the ring gear Ho-P2 of the second planetary gearset P2 of the main gearset HRS are arranged in the second Radsatzebene RSE-2.
  • the ring gear Ho-P4 of the planetary gearset P4 of the additional gearset ZRS and the ring gear Ho-P1 of the planetary gearset P1 of the main gearset HRS are formed as a common ring gear Ho-Z.
  • the sun So-P1 of the first planetary gearset P1 of the main gearset HRS and the sun So-P2 of the second planetary gearset P2 of the main gearset HRS are formed as a common sun So-Z.
  • the transmission G has an electric machine EM, wherein a stator S is non-rotatably connected to the transmission housing GG of the transmission G or with another non-rotatable component of the transmission G, so that the stator S can not assume any speed.
  • a rotatably mounted rotor R is connected to a sun So-P4 of the planetary gear set P4 of relieveradsatzes ZRS, wherein the sun gear So-P4 of the planetary gear set P4 of the sansradsatzes ZRS meshes with outer planetary gears (PA-P1) of the first planetary gear set P1 of the main gearset HRS.
  • the sun So-P4 of the planetary gear P4 of waiveradsatzes ZRS is part of a first wave W1 P4 of Rajradsatzes ZRS.
  • the web St-P4 of the planetary gear P4 of relieveradficientes ZRS is part of a second wave W2P4 of waiveradsatzes ZRS and is connected to the second wave W2 of the main gearset HRS.
  • the ring gear Ho-P4 of the planetary gear P4 of relieveradsatzes ZRS is part of a third wave W3P4 of waiveradsatzes ZRS and is connected to the third wave W3 of the main gearset HRS.
  • the transmission input shaft GW1 can be connected via a power path L1 via a first shifting element A to the fourth shaft W4 of the main gearset HRS and via a second shifting element E to the second shaft W2 of the main gearset HRS.
  • the first wave W1 of the main gearset HRS is rotatably fixed via a third switching element C.
  • the second wave W2 of the main gearset HRS is rotatably fixed via a fourth switching element D.
  • D is therefore a firm connection with a transmission housing GG of the transmission G or with another rotatably fixed component of the transmission G produced.
  • Fig. 2 shows a speed diagram of the first embodiment of the transmission G, while in Fig.
  • FIG. 3 is a circuit diagram of the first embodiment of the transmission G is shown.
  • the rotational speeds of the four shafts W1, W2, W3, W4 of the main gearset HRS and of the rotor R are plotted in the vertical direction in relation to the rotational speed of the transmission input shaft GW1.
  • the maximum occurring speed of the transmission input shaft GW1 is normalized to the value one.
  • the distances between the four shafts W1, W2, W3, W4 of the main gearset HRS and the rotor R result from the stationary gear ratios of the first and second planetary gear sets P1, P2 of the main gearset HRS and the stationary gear ratio of the planetary gearset P4 of the additional gearset ZRS.
  • Speed ratios associated with a particular operating point can be connected by a straight line.
  • Fig. 3 shows a circuit diagram of the transmission G according to the first embodiment.
  • the closed circuit elements A, C, D, E are indicated in FIG. 3 by circles.
  • the shift pattern, the respective translations of the individual gear ratios and the gear ratios to be determined from the next higher gear can be exemplified.
  • the translations result from the stationary gear ratios of the planetary P1, P2, P4.
  • With sequential switching mode, double circuits or group circuits can be avoided since two adjacent gear stages share a switching element.
  • the gears of the transmission G are shown in the various lines of the wiring diagram. In a column of the wiring diagram is further specified whether the electric machine EM in the gear in question is capable of delivering mechanical power to or from the transmission output shaft GW2.
  • a first forward gear 1 VM between the transmission input shaft GW1 and the transmission output shaft GW2 is obtained by closing the first shifting element A and the fourth shifting element D, a second forward speed 2VM closing the first shifting element A and the third shifting element C, a third forward speed 3VM by closing the first switching element A and the second switching element E, and a fourth forward speed 4VM closing the third switching element C and the second switching element E.
  • an electric gear 1 EM torque is transmitted solely from the electric machine EM to the transmission output shaft GW2, wherein all switching elements are open to the fourth switching element D, and thus no torque-carrying connection between the transmission input shaft GW1 and the transmission output shaft GW2 consists.
  • the electric gear 1 EM also serves as reverse gear, in which the electric machine EM is driven so that the rotor R assumes a negative speed, that is, a reverse rotation. On a separate reverse gear can thus be dispensed with.
  • the transmission input shaft GW1 torque is supplied.
  • the first switching element A and the fourth switching element D is closed, whereby the second wave W2 of the main gearset HRS is fixed rotationally fixed. If, in the first start mode, 1 S torque is applied to the transmission output shaft GW 2, then such power can be transmitted from the transmission output shaft GW 2 to the transmission input shaft GW 1.
  • the electric machine EM can also add power.
  • the first start mode 1 S can be used for towing start of the internal combustion engine VKM.
  • the second start mode 2S all switching elements are open except for the first switching element A.
  • Fig. 4 shows schematically a transmission G according to a second embodiment.
  • the transmission input shaft GW1 can be connected via the first shifting element A to the first shaft W1 of the main gearset HRS.
  • the transmission input shaft GW1 as well as in the first embodiment with the second wave W2 of the main gearset HRS connectable.
  • the first wave W1 of the main gearset HRS as in the first embodiment via the third switching element C rotatably fixed.
  • the fourth switching element D is in the second embodiment, the fourth wave W4 of the main gear HRS rotatably fixed.
  • Fig. 5 shows a speed diagram of the transmission G according to the second embodiment
  • Fig. 6 is a circuit diagram of the second embodiment of the transmission G is shown. The manner of illustration is identical to the first embodiment of the transmission G shown in FIGS. 2 and 3.
  • a total of four load-shiftable gears are formed between the transmission input shaft GW1 and the transmission output shaft GW2.
  • the first forward gear 1 VM between the transmission input shaft GW1 and the transmission output shaft GW2 is obtained by closing the fourth shift element D and the first shift element A, the second forward speed 2VM by closing the fourth shift element D and the second shift element E, the third forward speed 3VM by closing the second switching element E and the first switching element A, and the fourth forward gear 4VM by closing the third switching element C and the second switching element E.
  • the operation of the electric gear 1 EM, the starting modes 1 S, 2 S and the parking brake of the second embodiment is identical to the operation of the first embodiment.
  • Fig. 7 shows schematically a hybrid powertrain of a motor vehicle.
  • the transmission G contained therein corresponds to the second embodiment of the transmission G, this being merely exemplary.
  • a rotatable rotor R2 of an auxiliary electric machine SG is connected to the transmission input shaft GW1, while the stator S2 of the auxiliary electric machine SG is non-rotatably connected to the transmission case GG of the transmission G or to another non-rotatable component of the transmission G.
  • an internal combustion engine VKM is connected to the transmission input shaft GW1.
  • the gearbox output shaft GW2 is connected to a transaxle AG. Starting from the axle drive AG, the torque applied to the transmission output shaft GW2 is distributed to wheels W of the motor vehicle.
  • inverter INV In motor operation of the electrical Machine EM is fed to the stator S via an inverter INV electrical power.
  • the stator S supplies the inverter INV with electric power.
  • the inverter INV converts the DC voltage of a battery BAT into an AC voltage suitable for the electrical machine EM, and vice versa.
  • the additional electric machine SG can also be supplied with electrical power via the inverter INV.
  • the additional electric machine SG may also be connected to another power supply, for example to a low-voltage vehicle electrical system of the motor vehicle.
  • PA-P1 Outer planet gear of the first planetary gear set of the main gearset

Landscapes

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

Abstract

L'invention concerne une boîte de vitesses (G) comprenant un arbre d'entrée et un arbre de sortie (GW2), un essieu monté principal (HRS), un essieu monté additionnel (ZRS), et une machine électrique (EM) équipée d'un rotor (R) et d'un stator (S), la boîte de vitesses (G) comprenant au moins une voie de puissance (L1) placée entre l'arbre d'entrée (GW1) et l'essieu monté principal (HRS), l'essieu monté principal (HRS) comprenant des premier et deuxième ensembles de roues planétaires (P1, P2) comportant au total quatre arbres (W1, W2, W3, W4) désignés dans l'ordre des vitesses de rotation par premier, deuxième, troisième et quatrième arbre, l'au moins une voie de puissance (L1) pouvant être reliée, par au moins un élément de commutation (A, E), à l'un au moins des quatre arbres (W1, W2, W3, W4) de l'essieu monté principal (HRS), le troisième arbre (W3) de l'essieu monté principal (HRS) étant relié à l'arbre de sortie (GW2), l'essieu monté additionnel (ZRS) comprenant un ensemble de roues planétaires (P4) comportant des premier, deuxième et troisième arbres (W1P4, W2P4, W3P4), le premier arbre (W1P4) de l'essieu monté additionnel (ZRS) étant relié en permanence au rotor (R), le premier ensemble de roues planétaires (P1) de l'essieu monté principal (HRS) étant configuré sous la forme d'un ensemble de roues Plus et le deuxième ensemble de roues planétaires (P2) de l'essieu monté principal (HRS) étant configuré sous la forme d'un ensemble de roues Moins, un pivot (St-P1) du premier ensemble de roues planétaires (P1) de l'essieu monté principal (HRS), un pivot (St-P2) du deuxième ensemble de roues planétaires (P2) de l'essieu monté principal (HRS) et un pivot (St-P4) de l'ensemble de roues planétaires (P4) de l'essieu monté additionnel (ZRS) étant reliés entre eux, une couronne (Ho-P4) de l'ensemble de roues planétaires (P4) de l'essieu monté additionnel (ZRS) et une couronne(Ho-P1) du premier ensemble de roues planétaire (P1) de l'essieu monté principal (HRS) étant reliées entre elles, et une roue solaire (So-P4) de l'ensemble de roues planétaires (P4) de l'essieu monté additionnel (ZRS) s'engrenant avec des roues planétaires extérieures (PA-P1) du premier ensemble de roues planétaires (P1) de l'essieu monté principal (HRS).
PCT/EP2014/073881 2013-12-06 2014-11-06 Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique Ceased WO2015082168A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013225205.6A DE102013225205B4 (de) 2013-12-06 2013-12-06 Getriebe für ein Kraftfahrzeug
DE102013225205.6 2013-12-06

Publications (1)

Publication Number Publication Date
WO2015082168A1 true WO2015082168A1 (fr) 2015-06-11

Family

ID=51871017

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/073881 Ceased WO2015082168A1 (fr) 2013-12-06 2014-11-06 Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique

Country Status (2)

Country Link
DE (1) DE102013225205B4 (fr)
WO (1) WO2015082168A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180304896A1 (en) * 2015-10-20 2018-10-25 Exedy Corporation Driving apparatus for vehicle and vehicle
FR3098766A1 (fr) * 2019-07-17 2021-01-22 Punch Powerglide Strasbourg Transmission automatique pour véhicule hybride thermique/électrique
DE102020204639A1 (de) 2020-04-09 2021-10-14 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
WO2022258214A1 (fr) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Transmission pour un système d'entraînement électrique d'un véhicule à moteur et système d'entraînement électrique comprenant une telle transmission
DE102021205929A1 (de) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102022201820A1 (de) 2022-02-22 2023-08-24 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102022201821A1 (de) 2022-02-22 2023-08-24 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102022004536A1 (de) 2022-12-05 2024-06-06 Mercedes-Benz Group AG Bremssystem für ein Fahrzeug und Radbremsvorrichtung

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015210248A1 (de) 2015-06-03 2016-12-08 Zf Friedrichshafen Ag Getriebevorrichtung mit einer elektrischen Maschine
DE102015210251A1 (de) 2015-06-03 2016-12-08 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebstrang für ein Hybridfahrzeug mit einem solchen Getriebe
EP3100890A1 (fr) 2015-06-03 2016-12-07 ZF Friedrichshafen AG Dispositif d'entraînement doté d'une machine électrique
EP3100888A1 (fr) 2015-06-03 2016-12-07 ZF Friedrichshafen AG Boîte de vitesses d'un véhicule automobile, et groupe motopropulseur pour un véhicule hybride équipé d'une telle boîte de vitesses
DE102016202726B4 (de) * 2016-02-23 2018-01-11 Schaeffler Technologies AG & Co. KG Hochübersetzende Schaltgetriebeeinrichtung, insbesondere für ein elektrisch betriebenes Kraftfahrzeug
DE102016217248A1 (de) * 2016-09-09 2018-03-15 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug
DE102016217247A1 (de) 2016-09-09 2018-03-15 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug
DE102017222707B4 (de) 2017-12-14 2021-07-29 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1279543A2 (fr) * 2001-07-23 2003-01-29 Nissan Motor Co., Ltd. Chaîne motrice hybride pour véhicules
EP1375963A2 (fr) * 2002-06-17 2004-01-02 Nissan Motor Co., Ltd. Transmission hybride
EP1577141A2 (fr) * 2004-03-17 2005-09-21 Nissan Motor Co., Ltd. Commande de changement de mode de fonctionnement pour véhicule hybride

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3699694B2 (ja) * 2002-05-31 2005-09-28 日産自動車株式会社 ハイブリッド変速機
DE102012201377A1 (de) 2012-01-31 2013-08-01 Zf Friedrichshafen Ag Hybridantriebsstrang für ein Kraftfahrzeug

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1279543A2 (fr) * 2001-07-23 2003-01-29 Nissan Motor Co., Ltd. Chaîne motrice hybride pour véhicules
EP1375963A2 (fr) * 2002-06-17 2004-01-02 Nissan Motor Co., Ltd. Transmission hybride
EP1577141A2 (fr) * 2004-03-17 2005-09-21 Nissan Motor Co., Ltd. Commande de changement de mode de fonctionnement pour véhicule hybride

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180304896A1 (en) * 2015-10-20 2018-10-25 Exedy Corporation Driving apparatus for vehicle and vehicle
FR3098766A1 (fr) * 2019-07-17 2021-01-22 Punch Powerglide Strasbourg Transmission automatique pour véhicule hybride thermique/électrique
DE102020204639A1 (de) 2020-04-09 2021-10-14 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102021205927A1 (de) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102021205929A1 (de) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
WO2022258213A1 (fr) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Transmission pour une propulsion électrique d'un véhicule automobile et propulsion électrique comprenant une telle transmission
WO2022258214A1 (fr) 2021-06-11 2022-12-15 Zf Friedrichshafen Ag Transmission pour un système d'entraînement électrique d'un véhicule à moteur et système d'entraînement électrique comprenant une telle transmission
DE102022201820A1 (de) 2022-02-22 2023-08-24 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102022201821A1 (de) 2022-02-22 2023-08-24 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
WO2023160918A1 (fr) 2022-02-22 2023-08-31 Zf Friedrichshafen Ag Engrenage pour un système d'entraînement électrique d'un véhicule automobile et système d'entraînement électrique doté d'un tel engrenage
US11852224B2 (en) 2022-02-22 2023-12-26 Zf Friedrichshafen Ag Gear unit for an electric drive system of a motor vehicle and electric drive system with such a gear unit
DE102022201821B4 (de) * 2022-02-22 2025-11-27 Zf Friedrichshafen Ag Getriebe für ein elektrisches Antriebssystem eines Kraftfahrzeugs sowie elektrisches Antriebssystem mit einem solchen Getriebe
DE102022004536A1 (de) 2022-12-05 2024-06-06 Mercedes-Benz Group AG Bremssystem für ein Fahrzeug und Radbremsvorrichtung

Also Published As

Publication number Publication date
DE102013225205B4 (de) 2019-01-10
DE102013225205A1 (de) 2015-06-11

Similar Documents

Publication Publication Date Title
DE102013225205B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225209B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225208B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225212B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225202B4 (de) Getriebe für ein Kraftfahrzeug
DE102013227024B4 (de) Getriebe für ein Kraftfahrzeug
EP3077239B1 (fr) Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule automobile
DE102013225213B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225210B4 (de) Getriebe für ein Kraftfahrzeug
DE102013225207B4 (de) Getriebe für ein Kraftfahrzeug
DE102013227012B4 (de) Getriebe für ein Kraftfahrzeug
DE102013227021B4 (de) Getriebe für ein Kraftfahrzeug
DE102013227011B4 (de) Getriebe für ein Kraftfahrzeug
DE102015210249A1 (de) Getriebe für ein Kraftfahrzeug, sowie Antriebstrang für ein Hybridfahrzeug mit einem solchen Getriebe
WO2015090827A1 (fr) Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique
WO2015090837A1 (fr) Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule automobile électrique
WO2015090824A1 (fr) Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique
WO2015090836A1 (fr) Boîte de vitesses, chaîne cinématique hybride et chaîne cinématique pour véhicule électrique
DE102013227029A1 (de) Getriebe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14796039

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 14796039

Country of ref document: EP

Kind code of ref document: A1