WO2017148573A1 - Dispositif d'entraînement, notamment pour un véhicule électrique - Google Patents

Dispositif d'entraînement, notamment pour un véhicule électrique Download PDF

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Publication number
WO2017148573A1
WO2017148573A1 PCT/EP2017/000239 EP2017000239W WO2017148573A1 WO 2017148573 A1 WO2017148573 A1 WO 2017148573A1 EP 2017000239 W EP2017000239 W EP 2017000239W WO 2017148573 A1 WO2017148573 A1 WO 2017148573A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
transmission
gear
drive
switching unit
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/EP2017/000239
Other languages
German (de)
English (en)
Inventor
Tobias Schilder
Josep Maria Bou Romano
Klaus Riedl
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler AG filed Critical Daimler AG
Publication of WO2017148573A1 publication Critical patent/WO2017148573A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—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
    • 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
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • 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
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • 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
    • 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
    • F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
    • 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
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three 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
    • 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
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
    • 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
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the invention relates to a drive device for a motor vehicle, in particular an electric vehicle or a motor vehicle with at least one purely electrically driven drive axle.
  • WO 2012/010340 A1 already discloses a drive device for an electric vehicle, which has an electric motor, an axle drive and a multi-speed transmission arranged between the electric motor and the final drive.
  • a drive device with three planetary gear stages wherein a transmission input element permanently rotatably connected to a second sun gear, a transmission output member permanently rotatably connected at least with a third planet carrier and a
  • Switching unit is provided to lock the third planetary gear, a second planet carrier and a third ring gear are permanently connected to each other rotatably, a first planet carrier is fixed to the housing
  • the invention is in particular the object of a further developed
  • Electric vehicle with at least one final drive and with one between one
  • Circuit of three forward gears provided multi-speed transmission, the exactly three operatively interconnected Planetenradmen with sun gears, ring gears and planet carriers, three switching units with two rotatably interconnected coupling elements, a transmission input element for non-rotatable connection of the electric motor and a transmission output member for rotationally fixed connection of the final drive, wherein the transmission input element permanently rotatably connected to the sun gear of the second planetary gear, the transmission output element permanently rotatably connected at least to the planet carrier of the third planetary gear and the third switching unit is provided to lock the third planetary gear.
  • the sun gear of the first planetary gear and the ring gear of the second planetary gear are permanently connected to each other in a rotationally fixed manner.
  • Electric motor allows the final drive. Through the multi-speed transmission, different forward gears can be provided, by which a given by the electric motor drive torque can be implemented advantageously. On a shiftability of reverse gears can be omitted by the
  • Electric motor is provided for a reversal of direction.
  • Component loads can be at least partially reduced in the proposed multi-speed transmission by the basic structure, which in particular a lightweight construction can be simplified. Due to the differently translated forward gears, the electric motor can be operated with high efficiency even at high vehicle speeds. At low speeds, a torque of the electric motor can be implemented advantageously. Transmission ratios of the forward gears and / or the final drive can be at least partially adapted to a configuration of the electric vehicle. It can be a flexible drive device
  • a "drive device with at least one electric motor, with at least one axle drive and a multi-speed transmission arranged between the electric motor and the final drive” is intended in particular to mean a
  • Drive device which has only electric motors for generating a drive torque.
  • it should include one of a
  • a "multistage transmission” is to be understood as meaning, in particular, a transmission arranged between the electric motor and the final drive for shifting the engine
  • Planetary gear guided planetary gear and / or a meshing engagement between a guided by a planet carrier planetary gear and a ring gear is defined.
  • the planetary gear stages can be made at least partially in one piece.
  • two of the planetary gear have a common ring gear and separate sun gears or a common sun gear and separate ring gears.
  • final drive should be understood to mean, in particular, an operative connection between the transmission output element of the multistage transmission and at least one drive wheel of the motor vehicle
  • first planetary gear stage first planetary gear stage
  • second planetary gear stage second planetary gear stage
  • the designations "first”, “second” and “third” planetary gear stages are intended in particular for defining an axial arrangement, wherein an axial order of the planetary gear stages may deviate from the numbering, basically a modified arrangement of the planetary gear stages and / or a stacked arrangement
  • the kinematically equivalent transmission structures can be implemented in particular by a spatial rearrangement of the shifting units, by a changed arrangement of gear elements and / or by interchanging of the sun gears, planet gears and / or ring gears Transmission structures "should
  • Transmission structures are understood, which have an equal number of switching units and identical circuit diagrams for switching the forward gears and the reverse gears.
  • a switching unit is to be understood as meaning a unit having exactly two coupling elements which are rotatable relative to each other and which are provided for non-rotatable connection with one another
  • a switching unit is to be understood, which is arranged in a power flow between two of the planetary gear stages and which is intended to its two rotatably arranged coupling elements, which in a open state are independently rotatable, rotatably connected in a closed state with each other.
  • a switching unit which is designed as a "brake” should be understood in particular a switching unit, the
  • non-rotatably connected is meant in particular a connection in which a power flow over a complete revolution averaged with an unchanged torque, an unchanged direction of rotation and / or an unchanged speed is transmitted.
  • a switching unit should in particular not be understood as meaning a coupling which is connected upstream or downstream from a gear set formed by the planetary gear stages.
  • a "clutch upstream of the gear train” is to be understood in particular as a clutch that is in at least one gear in a power flow between the electric motor and the
  • Transmission input element is arranged, such as a separating clutch or a starting clutch.
  • a "clutch following the gear set” is to be understood in particular a clutch which is arranged in at least one gear in a power flow between the transmission output element and a final drive, such as an all-wheel drive
  • Switchability of the stepping gear by a gear set upstream or downstream coupling unit can be increased. Under a
  • a “transmission input element” is to be understood as meaning, in particular, a transmission element which is provided at least structurally for connection to a rotor of the electric motor in a rotationally fixed connection
  • a “transmission element” is to be understood in particular an embodiment which is provided for permanent non-rotatable connection between the sun gears, planetary carriers, ring gears and / or coupling elements.
  • Transmission gear is omitted or not.
  • the switching units may be structurally provided for switching more forward gears, as it may be useful to switch them as part of an operating strategy for the multi-speed transmission.
  • blocking a planetary gear is to be understood in particular that the sun gear, the planet carrier and the ring gear of a single
  • Switching unit for blocking a planetary gear should be understood to mean a single switching unit with two coupling elements, each with the sun gear, the planet carrier or the ring gear of the corresponding
  • Planetenradkg are permanently connected rotationally fixed, whereby the corresponding planetary gear can be blocked by closing this one switching unit.
  • the individual coupling unit for blocking the planetary gear can also be replaced by two coupling units connected in series.
  • a part of the switching units is formed positively.
  • a drag loss can be kept low, whereby a power loss within the multi-speed transmission can be advantageously reduced.
  • trained switching unit "should be understood in particular a switching unit, which is used to connect their coupling elements or to connect their
  • Coupling element has a toothing and / or claws, which interlock positively to produce a rotationally fixed connection, wherein a transfer of a power flow in a fully closed state is at least mainly by a positive connection.
  • the switching units can in principle be formed frictionally or positively. Under a "frictionally trained
  • Switching unit “should be understood in particular a switching unit, which has at least two friction partners for connecting their coupling elements or to connect their coupling element, which rest against one another to produce a rotationally fixed connection frictionally, wherein a transmission of a power flow in a fully closed state, at least mainly by friction
  • a frictionally engaged coupling unit is preferably as one Multi-plate clutch unit and a friction-trained brake unit is preferably designed as a multi-disc brake unit.
  • trained coupling unit is preferably as a dog clutch unit and a form-locking trained braking unit is preferably as a
  • a form-fitting trained switching unit is advantageously switchable via a sliding sleeve.
  • the form-fitting trained switching units are preferably carried out without a frictional synchronization, but in principle may also have a frictional synchronization.
  • the multistage transmission preferably comprises actuators for the automated switching of the switching units.
  • actuators for the automated switching of the switching units.
  • An independently switching coupling unit or braking unit is preferably designed as a freewheel.
  • Double planetary gear set to replace, in addition to a kinematic same mode of action in particular a stand ratio of the planetary gear must be adjusted.
  • Double planetary gear set to replace, in addition to a kinematic same mode of action in particular a stand ratio of the planetary gear must be adjusted.
  • Double planetary gear set to replace, in addition to a kinematic same mode of action in particular a stand ratio of the planetary gear must be adjusted.
  • Main axis of rotation runs.
  • radial refers in particular to a direction which is perpendicular to the main axis of rotation
  • the said component is arranged on one side of the further component which faces the transmission input element and / or the electric motor Side of the further component is arranged, which faces away from the transmission input element and / or the electric motor, even if the further component is arranged in the axial direction after the transmission output element, for example, because the transmission output element is arranged between two planetary gear stages.
  • Fig. 1 shows a motor vehicle with a drive device which has an electric motor and a
  • FIG. 3 is a circuit diagram for the multi-speed transmission of Fig. 2,
  • Fig. 4 shows a transmission scheme with planetary gear stages in a modified arrangement
  • Fig. 5 is a transmission diagram with Planetenradkgm which are partially stacked.
  • FIG. 1 shows a motor vehicle with a drive device.
  • the drive device is provided for an electric motor drive of the motor vehicle.
  • the motor vehicle can be designed as a pure electric vehicle.
  • the drive device is provided only for the electric motor drive. In principle, it is conceivable that the drive device with a second drive device for a
  • Combustion engine drive is combined.
  • proposed drive device which is provided for the electric motor drive, act on a first drive axle of the motor vehicle, while the
  • the drive device comprises an electric motor 10a, an axle drive 11a and a between the electric motor 10a and the final drive 11 a arranged
  • the electric motor 10a may be a permanent-magnet synchronous machine or a permanent magnet asynchronous machine.
  • Multi-speed transmission 12a is provided at least structurally for shifting three differently translated forward gears V1a, V2a, V3a.
  • Multi-stage transmission 12a has exactly three planetary gear stages Pia, P2a, P3a.
  • the multi-stage transmission 12a has a main axis of rotation to which the first
  • a number of the forward gears V1a, V2a, V3a actually used may be limited depending on an operating strategy, for example electronically by a suitably programmed control unit.
  • a drive device in which the multistage transmission 12a is combined with a drive unit in the form of an internal combustion engine.
  • the internal combustion engine then either replaces the electric motor 12a as a drive unit or the internal combustion engine is used together with the electric motor 12a as the drive unit.
  • the multi-stage transmission 12a has exactly three switching units S1a, S2a, S3a, which are provided for switching the forward gears V1 a, V2a, V3a.
  • Multi-stage transmission 12a has a transmission housing 15a, which receives the planetary gear stages Pi a, P2a, P3a and the switching units S1a, S2a, S3a.
  • the switching units S1a, S2a, S3a are operatively arranged within a gear set formed by the planetary gear stages Pia, P2a, P3a, i. the switching units S1a, S2a, S3a are intended to produce different operative connections between the planetary gear stages Pia, P2a, P3a with each other and / or between the planetary gear stages Pia, P2a, P3a and the gearbox 15a.
  • the circuit diagram shown in Figure 3 shows how the forward gears V1a, V2a, V3a are switched by closing the switching units S1a, S2a, S3a.
  • the Forward gears V1a, V2a, V3a are each switched by closing one of the three shift units S1a, S2a, S3a.
  • Each of the switching units S1a, S2a, S3a is associated with exactly one of the forward gears V1a, V2a, V3a.
  • a load circuit between two of the forward gears V1a, V2a, V3a is in this case always possible in particular when at most one of the switching units S1a, S2a, S3a is closed in a switching operation and / or at most one of the
  • Switching units S1a, S2a, S3a is opened, i. when a power flow from one of the switching units S1a, S2a, S3a is given to another of the switching units S1a, S2a, S3a, or when a switching state of only one of the switching units S1a, S2a, S3a is changed.
  • the three forward gears V1a, V2a, V3a are
  • the multistage transmission 12a connects the electric motor 10a to the final drive 1a of the motor vehicle.
  • the multi-stage transmission 12 a can be
  • the multi-stage transmission 12a has a transmission input member 13a provided to output from the electric motor 10a
  • the electric motor 10a comprises a rotor, which in the illustrated embodiment is permanently non-rotatably connected to the transmission input element 13a.
  • the transmission input member 13a may be formed differently, such as a shaft or a flange.
  • the multistage transmission 12a has a transmission output element 14a, which is provided to discharge a drive torque from the multistage transmission 12a.
  • the final drive 11a has in the illustrated embodiment
  • Transmission output element 14a is connected.
  • the final drive 11a is provided to distribute the drive torque provided by the electric motor 10a to the two drive wheels of the drive axle.
  • the electric motor 10a it is also conceivable that the electric motor 10a can be used to distribute the drive torque provided by the electric motor 10a to the two drive wheels of the drive axle.
  • Transmission output element 14a permanently rotatably connected to an axle shaft and / or one of the drive wheels.
  • Final drive 11 a be arranged at least one other module, such as an all-wheel drive module, the drive torque on two different drive axles distributed.
  • the transmission output member 14a may be formed differently, such as a shaft, a spur gear or a pinion.
  • the transmission input member 13a and the transmission output member 14a are arranged coaxially with the main rotation axis.
  • the transmission input element 13a is arranged on a side facing the electric motor 10a side of the multi-speed transmission 12a.
  • For the transmission output member 14a are basically in the axial direction
  • the planetary gear stages Pi a, P2a, P3a are arranged between the transmission input element 13a and the transmission output element 14a.
  • Planetary gear stages Pi a, P2a, P3a are arranged one behind the other in the axial direction. To redesign the multi-stage transmission 12a, it is possible to change the order of the
  • the multi-stage transmission 12a has three levels in which the planetary gear stages Pi a, P2a, P3a are arranged. A numbering of the level corresponds to an order of the levels, which is referred to below on the transmission input member 13a.
  • the first plane has a smaller distance to the electric motor 10a than the third plane.
  • the first planetary gear stage Pi a is arranged along the main axis of rotation in the first plane.
  • the first planetary gear stage Pi a has a109planetenradsatz and includes a sun gear P1 1 a, a ring gear P13a and a planet P12a.
  • the planet carrier P12a leads planetary gears P14a on a circular path.
  • the planet gears P14a mesh with the sun gear P1 1 a and with the ring gear P13a.
  • the planetary gears P14a are rotatably supported on the planet carrier P12a.
  • the second planetary gear P2a is disposed along the main rotation axis in the second plane.
  • the second planetary gear P2a is along the main axis of rotation on a side facing away from the transmission input member 13a side of the first
  • the second planetary gear P2a has a
  • the planet P22a leads planetary gears P24a on a circular path.
  • the planetary gears P24a mesh with the sun gear P21a and with the ring gear P23a.
  • the planetary gears P24a are rotatably supported on the planet carrier P22a.
  • the third planetary gear P3a is arranged along the main rotation axis in the third plane.
  • the third planetary gear P3a is arranged along the main axis of rotation on a side facing away from the transmission input member 13a side of the second planetary gear P2a.
  • the third planetary gear P3a has a109planetenradsatz and includes a sun gear P31a, a ring gear P33a and a planet P32a.
  • the planet carrier P32a leads planetary gears P34a on a circular path.
  • the planet gears P34a mesh with the sun gear P31a and with the ring gear P33a.
  • the planetary gears P34a are rotatably supported on the planet carrier P32a.
  • the switching units S1a, S2a, S3a are designed as brakes.
  • the switching units S1a, S2a designed as brakes each have a rotatably mounted one
  • the switching units S1a, S2a are each provided to rotatably support their rotatably mounted coupling element S11 a, S21 a with the transmission housing 15a to connect.
  • Switching units S1a, S2a is permanently connected in a rotationally fixed manner to at least one of the sun gears P11a, P21a, P31a, one of the planetary carrier P12a, P22a, P32a and / or one of the ring gears P13a, P23a, P33a.
  • the housing fixed arranged
  • Coupling elements S12a, S22a of the switching units S1a, S2a are permanently non-rotatably connected to the transmission housing 15a.
  • the remaining switching unit S3a is designed as a clutch.
  • the switching unit S3a designed as a coupling has a first rotatably mounted coupling element S31a and a second rotatably mounted coupling element S32a.
  • the switching unit S3a is provided to connect their two coupling elements S31a, S32a rotationally fixed to each other.
  • Each of the coupling elements S31 a, S32a of the switching unit S3a is connected to at least one of the sun gears P11a, P21a, P31a, one of the
  • Coupling elements S11 a, S12a, S21a, S22a, S31a, S32a includes the
  • Multi-stage transmission 12a a plurality of transmission elements 16a, 17a, 18a, 19a.
  • the four gear elements 16a, 17a, 18a, 19a are provided to torque and / or rotational movements within the through the planetary gear Pia, P2a, P3a
  • Transmission elements 16a, 17a, 18a, 19a connects at least two of the sun gears P1 1a, P21a, P31a, planetary gear P12a, P22a, P32a, ring gears P13a, P23a, P33a and / or coupling elements S1 1a, S12a, S21a, S22a, S31a, S32a permanently rotationally fixed to each other or supports at least one of the sun gears P1 1a, P21 a, P31 a .
  • Planet wheel P12a, P22a, P32a and / or ring gears P 3a, P23a, P33a permanently against the gear housing 15a from.
  • the transmission input element 13a forms a transmission input shaft, which permanently interconnects the transmission input element 13a and the sun gear P21a of the second planetary gear P2a with each other.
  • the transmission input element 13a is connected on the input side to the sun gear P21a.
  • the transmission output member 14a forms a transmission output shaft that includes the transmission output member 14a and the planet carrier P32a of the third
  • Transmission output member 14a formed transmission output shaft passes through the sun P31 a of the third planetary gear P3a and is for the connection of the
  • the transmission element 16a forms an intermediate shaft, which is the first coupling element S1 1a of the first switching unit S1a, the planet carrier P22a of the second
  • the transmission element 16a is guided in each case radially outward.
  • the formed by the transmission element 16a intermediate shaft limits the gear set transmission input side.
  • the transmission element 17a forms an intermediate shaft which is the sun gear P31a of the third planetary gear P3a, the second coupling element S32a of the third
  • the intermediate shaft formed by the transmission element 17a encloses the planetary gear stages P2a, P3a. It limits the gear set on the output side.
  • the transmission element 18a forms an intermediate shaft which permanently rotatably connects the sun gear P1 1a of the first planetary gear set Pi a and the ring gear P23a of the second planetary gear set P2a.
  • the transmission element 18a is guided radially outward between the planetary gear stages Pia, P2a.
  • the transmission element 19a forms a connection which connects the planet carrier P22a of the second planetary gear P2a and the transmission housing 15a permanently rotatably together.
  • the planet carrier P22a is thereby fixed to the housing.
  • the first switching unit S1a is arranged in the axial direction on the transmission input side of the first planetary gear stage Pia.
  • the second switching unit S2a is arranged axially in the amount of the first planetary gear Pi a.
  • the third switching unit S3a is axial
  • the first switching unit S1a is provided to the planet carrier P22a of the second planetary gear P2a and the ring gear P33a of the third planetary gear P3a
  • the second switching unit S2a is provided to the ring gear P23a of the second planetary gear P2a and the sun gear P31a of the third
  • the third switching unit S3a is provided to the sun gear P31 a of the third planetary gear P3a and the
  • Planet carrier P32a the third planetary gear P3a rotatably connect with each other. If the third switching unit S3a is closed, the sun gear P31a and the planet carrier P32a of the third planetary gear P3a are non-rotatable with each other
  • the third switching unit S3a may also be provided for permanently connecting the sun gear P31a and the ring gear P33a of the third planetary gear stage P3a or the planetary gear carrier P32a and the ring gear P33a of the third planetary gear stage P3a in a rotationally fixed manner.
  • All switching units S1a, S2a, S3a are outboard, i. a
  • Actuator supply of the switching units S1a, S2a, S3a can be realized without carrying out operating medium lines by a rotatably mounted component. None of the switching units S1a, S2a, S3a are internal, i. requires one
  • Switching units S1 a, S2a, S3a are hydraulically actuated.
  • the differential gear whose outputs are arranged coaxially with the main axis of rotation of the multi-speed transmission 12a (see Figure 1).
  • Final drive 1 1 a also two axle shafts for driving the drive wheels of a
  • the final drive 1 1 a on a main axis of rotation which is coaxial with the main axis of rotation of the
  • Multi-stage transmission 12a is arranged.
  • one of the axle shafts passes through at least the transmission input element 13a and the electric motor 10a.
  • the final drive 11a is possible to integrate the multi-stage transmission 12a. Nesting of the multi-stage transmission 12a and the final drive 1 1 a depends in particular on a position of the differential gear along the
  • Embodiment in which the final drive 1 1 a is provided for a direct connection of only one drive wheel, it is conceivable to pass the transmission output member 14a in the form of an inner shaft through the transmission input member 13a and the electric motor 10a, whereby the electric motor 10a between the drive wheel and the Multi-step transmission 12a is arranged.
  • Figure 4 shows a second embodiment of a transmission scheme of a
  • Multi-speed transmission 12b for a drive device with an electric motor and a final drive.
  • the multistage transmission 12b is at least structurally provided for shifting three forward gears.
  • the transmission scheme is structurally similar to that of the first embodiment.
  • the multistage transmission 12b comprises a transmission input element 13b for the rotationally fixed connection of the electric motor and a transmission output element 14b for the rotationally fixed connection of the final drive.
  • the multi-stage transmission 12b includes a
  • the multi-stage transmission 12b comprises three switching units S1b, S2b, S3b, each having two coupling elements S11b, S12b, S21b, S22b, S31b, S32b.
  • the multistage transmission 12b comprises a plurality of transmission elements 16b, 17b, 18b, 19b.
  • the multi-stage transmission 12b differs in particular in an arrangement of the planetary gear P1, P2b, P3b from that of the first embodiment.
  • Multi-stage transmission 12b has three levels in which the planetary gear P1, P2b, P3b are arranged.
  • the second planetary gear P2b is in the first plane
  • the first planetary gear P1 b is disposed in the second plane.
  • the third planetary gear P3b is arranged in the third plane.
  • the first planetary gear P1 b is in the axial direction between the second planetary gear P2b and the third
  • Planet wheel P3b arranged.
  • the rearrangement of the planetary gear P1, P2b results in a modified arrangement of the transmission elements 16b, 17b, 18b, 19b.
  • the first switching unit S1 b is arranged on the input side of the second planetary gear P2b.
  • the switching unit S2b is arranged axially in the amount of the second planetary gear P2b.
  • Figure 5 shows a third embodiment of a transmission scheme of a
  • Multi-stage transmission 12 c for a drive device with an electric motor and a final drive.
  • the multistage transmission 12c is at least structurally provided for shifting three forward gears.
  • the transmission scheme is structurally similar to that of the first embodiment.
  • the multistage transmission 12c comprises a transmission input element 13c for the non-rotatable connection of the electric motor and a transmission output element 14c for the rotationally fixed connection of the final drive.
  • the multi-stage transmission 12c includes a
  • Gear set comprising a first planetary gear set P1c, a second planetary gear set P2c and a third planetary gear set P3c, each comprising a sun gear P11c, P21c, P31c, a ring gear P13c, P23c, P33c and a planet carrier P12c, P22c, P32c, which planet gears P14c, P24c, P34c in a circular orbit around the corresponding sun P11c, P21c, P31c leads, have.
  • the multi-stage transmission 12c comprises three switching units Sic, S2c, S3c, each having two coupling elements S1 1c, S12c, S21c, S22c, S31c, S32c.
  • the multi-stage transmission 12c includes a plurality of transmission elements 16c, 17c, 18c, 19c.
  • the multi-stage transmission 12c is different in particular from an arrangement of the planetary gear stages P1c, P2c, P3c from that of the first embodiment. in the
  • the first planetary gear stage P1c and the third planetary gear stage P3c are arranged stacked.
  • the multi-stage transmission 12c has two levels in which the planetary gear P1, P2c, P3c are arranged.
  • the second planetary gear P2c is arranged in the first plane.
  • Planetary gear P1 c and the third planetary gear P3c are arranged in the second plane.
  • the first planetary gear P1c is radially inside the third
  • the first switching unit Sic is arranged in the axial direction of the transmission input side of the second planetary gear P2c.
  • Switching unit S2c and the third switching unit S3c are arranged in the axial direction between the first plane in which the second planetary gear P2c is arranged, and the second plane in which the planetary gear P1, P3c are arranged.
  • the first switching unit S1a, S1b, Sic is particularly advantageously designed as a form-locking switching unit.
  • the design as the first switching unit S1a, S1b, Sic as a form-locking switching unit shows that an efficiency of the drive device can be increased, whereby overall an acceptable shifting comfort can still be achieved. Furthermore, the efficiency of the drive device can be further increased by the fact that in each case the third switching unit S3a, S3b, S3c is designed as a form-locking switching unit. Also hereby an acceptable shifting comfort can still be achieved.

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

Abstract

L'invention concerne un dispositif d'entraînement, comprenant au moins un entraînement d'essieu (11a- c) et une boîte de vitesses multi-étagée (12a-c), qui est agencée entre un élément d'entrée et l'entraînement d'essieu (11a-c), est destinée au changement, au moins structurel, de trois rapports de marche avant (V1 a-c, V2a-c, V3a-c), et comprend exactement trois étages de planétaire (P1a-c, P2a-c, P3a-c) reliés fonctionnellement et qui présentent des pignons planétaires (P11a-c, P21a-c, P31a-c), des couronnes (P13a-c, P23a-c, P33a-c) et des porte-satellites (P12a-c, P22a-c, P32a-c), trois unités de changement de vitesse (S1a-c, S2a-c, S3a-c) présentant chacune deux éléments d'accouplement (S11a-c, S12a- c, S21a-c, S22a-c, S31a-c, S32a-c) pouvant être reliés l'un à l'autre de manière solidaire en rotation, un élément d'entrée (13a-c) de boîte destiné à être relié de manière solidaire en rotation au moteur électrique (10a-c) et un élément de sortie (14a-c) de boîte destiné à être relié de manière solidaire en rotation à l'entraînement d'essieu (11a-c). L'élément d'entrée (13a-c) de boîte est relié de manière permanente et solidaire en rotation au pignon planétaire (P21a-c) du deuxième étage de planétaire (P2a-c), l'élément de sortie (14a-c) de boîte est relié de manière permanente et solidaire en rotation au moins au porte-satellite (P32a-c) du troisième étage de planétaire (P3a-c) et la troisième unité de changement de vitesse (S3a-c) est conçue pour bloquer le troisième étage de planétaire (P3a-c).
PCT/EP2017/000239 2016-03-03 2017-02-20 Dispositif d'entraînement, notamment pour un véhicule électrique Ceased WO2017148573A1 (fr)

Applications Claiming Priority (2)

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DE102016002567.0A DE102016002567B4 (de) 2016-03-03 2016-03-03 Antriebsvorrichtung, insbesondere für ein Elektrofahrzeug
DE102016002567.0 2016-03-03

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DE102018210949A1 (de) * 2018-07-03 2020-01-09 Zf Friedrichshafen Ag Antriebsvorrichtung für zumindest eine elektrisch angetriebene Achse eines Kraftfahrzeugs
KR102566923B1 (ko) * 2021-04-29 2023-08-16 현대모비스 주식회사 동력 전달 장치 및 그 동력 전달 장치를 포함하는 자동차

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CN111819374B (zh) * 2018-02-23 2024-04-02 戴姆勒卡车股份公司 用于机动车尤其是汽车的电驱动装置

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