WO2021013301A1 - Dispositif d'entraînement pour un véhicule à moteur comprenant au choix un porte-satellite commutable solidaire du boîtier ou une couronne - Google Patents

Dispositif d'entraînement pour un véhicule à moteur comprenant au choix un porte-satellite commutable solidaire du boîtier ou une couronne Download PDF

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Publication number
WO2021013301A1
WO2021013301A1 PCT/DE2020/100625 DE2020100625W WO2021013301A1 WO 2021013301 A1 WO2021013301 A1 WO 2021013301A1 DE 2020100625 W DE2020100625 W DE 2020100625W WO 2021013301 A1 WO2021013301 A1 WO 2021013301A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
drive device
ring gear
drive
planetary
Prior art date
Application number
PCT/DE2020/100625
Other languages
German (de)
English (en)
Inventor
Franz Voelkel
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2021013301A1 publication Critical patent/WO2021013301A1/fr

Links

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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
    • F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction 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
    • F16H2200/0021—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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

Definitions

  • the invention relates to a drive device for a motor vehicle, in particular for an electrically driven motor vehicle, with an electric drive machine which is operatively connected to a transmission device via a drive shaft, the transmission device having at least a first and second planetary gear stage and a differential stage, the first planetary gear stage having a having the first planetary gear set with several planetary gears, the planetary gears of the first planetary gear set being rotatably arranged on a first planetary gear carrier and meshing with a first sun gear and with a first ring gear, where the second planetary gear set has a second planetary gear set with several planetary gears, wherein the planet gears of the second planetary gear set are rotatably arranged on a second planet carrier and with a second sun wheel and with a second ring gear are in meshing engagement, the first and the zw eite planetary gear stage are operatively connected to a double clutch device with a first and a second power shiftable clutch.
  • DE 10 2011 088 668 A1 shows a drive device with at least one electric drive machine, with at least one first planet driven with a clutch and with a differential.
  • a rotor shaft of the drive machine is rotatably coupled to a first connection shaft of the planetary drive formed from at least three connection shafts.
  • a second connection shaft of the first planetary drive can be fixed in a rotationally fixed manner by means of a shift sleeve of the clutch against a component of the drive device.
  • a third connection shaft of the first planetary drive is connected to a sum shaft of the differential.
  • DE 10 2013 225 519 A1 shows a planetary gear, in particular for a motor vehicle, with an input shaft forming a sun gear, with a planet gear carrier that carries a first set of planet gears and a second set of planet gears, with a first ring gear , which is assigned to the first set of planetary gears, with a second ring gear, which is assigned to the second set of planetary gears, with a first locking means, by means of which the first ring gear can be locked, and with a second locking means, by means of which the second ring gear can be locked .
  • a transmission device with a CVT transmission and with a differential is shown therein, wherein the CVT transmission has a CVT transmission stage with variable transmission between a power input shaft and a power output shaft and wherein the power output shaft and an input shaft of the differential are coupled to one another and the differential is provided with at least a first output shaft and a second output shaft.
  • the prior art has the disadvantage that, due to a complex transmission structure, a large number of different parts and components are installed and therefore the manufacturing costs increase and assembly is made more difficult.
  • a drive device for a motor vehicle is to be further developed, the focus being on a transmission structure that is as simple as possible with many identical parts and a suitable gear ratio distribution or spread.
  • the drive device according to the invention for a motor vehicle comprises an electrical cal drive machine which is operatively connected to a transmission device via a drive shaft.
  • the transmission device has at least a first and second planetary gear set as well as a differential stage, the first planetary gear set having a first planetary gear set with several planet gears, the planet gears of the first planetary gear set being rotatably arranged on a first planetary gear carrier and with a first sun gear and a first Ring gear are in meshing engagement, the second planetary gear set having a second planetary gear set with several Pla designated gears, wherein the planet gears of the second planetary gear set are rotatably arranged on a second planetary gear carrier and are in meshing engagement with a second sun gear and a second ring gear, and the first and the second planetary gear stage are operatively connected to a dual clutch device with a first and a second power shiftable clutch.
  • operatively connected is to be understood as meaning that two transmission elements can be directly connected to one another, or that further transmission elements are located between two transmission elements, for example one or more shafts or gears.
  • Two toothed meshing or meshing gears are provided for transmitting a torque and a speed from the egg NEN gear to the other gear.
  • a gear is to be understood, for example, as a sun gear, a ring gear and a planet gear of a planet gear set.
  • a double clutch device is to be understood as a device with two power shift clutches.
  • the term “powershiftable clutch” is to be understood as a device which has at least one open and one closed state and can be switched between the at least two states under load. When open, the clutch does not transmit any torque.
  • first ring gear and the second ring gear can be rigidly connected to one another to form a common ring gear.
  • first ring gear and the second ring gear or the common ring gear can have the same toothing. If the first ring gear and the second ring gear form the common ring gear, according to the invention the common ring gear can be fixed in place on the housing via the second clutch.
  • the first sun gear is non-rotatably connected to the drive shaft.
  • the first planet carrier can be rotatably connected to the second Son nenrad.
  • the first planet carrier and the second sun gear can preferably be operatively connected to the differential stage.
  • the first ring gear can be connected non-rotatably to the second planet carrier.
  • an advantageous embodiment can also be characterized in that an additional reduction gear is arranged in the torque flow between the electric drive machine and the differential stage.
  • the reducing transmission can be arranged on the input side between the electric drive machine and the first planetary gear stage or on the output side between the second planetary gear stage and the differential stage.
  • the additional reduction gear increases the spread of the transmission device and can be designed, for example, as a spur gear stage or as a further planetary gear stage.
  • the first and second clutch of the double clutch device can preferably be designed as a friction clutch.
  • the two couplings can preferably be arranged coaxially to one another.
  • the actuator can be designed hydraulically, electromechanically, electro-magnetically or, for example, also pneumatically.
  • the first gear ratio is preferably not equal to the second gear ratio.
  • the first gear ratio can be greater than the second gear ratio.
  • the first gear ratio can be smaller than the second gear ratio.
  • the electric drive machine preferably has a stator and a rotor, the rotor being non-rotatably connected to the drive shaft.
  • the drive shaft can be designed as a rotor shaft or there is an axial offset between the drive shaft and the rotor shaft, a torque transmission device (gearbox) being arranged between the two shafts.
  • the differential stage is preferably designed as a spur gear differential, the differential stage being provided to distribute a drive power of the drive machine to a first and a second output shaft.
  • the drive machine can be arranged coaxially or axially parallel to the differential stage.
  • the drive shaft is preferably attached coaxially to the two output shafts. arranges.
  • the drive shaft is designed as a hollow shaft, at least one of the two output shafts being guided axially through the drive shaft.
  • the two output shafts are net angeord on a common drive axle.
  • the drive shaft is axially parallel to the two output shafts, whereby axially parallel means that there is an axial offset between the drive shaft and the output shafts.
  • the invention relates to an axially parallel two-speed transmission for electric axles with a centrally installed shift element (Doppelkupplungsvorrich device).
  • the aim is to provide the simplest possible gear structure with many identical parts and suitable gear ratio distribution or spreading through a combination of two planetary gear stages with a spur gear stage and a shifting element designed as a double clutch or synchro unit, with the switching element for moderate speeds and torques is arranged in the middle of the power flow.
  • a first example includes a common ring gear, the fixed shaft optionally being the ring gear or the planetary gear carrier of the second planetary gear set.
  • the example can be modified according to the invention by a slightly different basic structure of the planetary gear sets.
  • FIG. 1 shows a first embodiment of the drive device according to the invention in an axially parallel construction
  • Fig. 2 shows a first modification of the drive device according to the first embodiment form in a coaxial design
  • FIG. 3 shows a second embodiment of the drive device according to the invention in an axially parallel construction
  • Fig. 4 shows a first modification of the drive device according to the second Austre approximately in a coaxial design.
  • Fig. 1 shows a first embodiment of the drive device 1 according to the invention in an axially parallel construction.
  • the drive device 1 according to the invention for a motor vehicle - not shown here - has an electric drive machine - not shown here - and a transmission device 3.
  • the electric drive machine has a stator and a rotor.
  • a drive power of the electric drive machine is introduced into the transmission device 3 via a drive shaft 2, which is arranged between the electric drive machine and the transmission device 3 and is designed as a rotor shaft.
  • the transmission device 3 comprises a first and second planetary gear stage 4, 5 and a differential stage 6.
  • the first planetary gear stage 4 has a first planetary gear set with several planetary gears 7a, which are rotatably arranged on a first planetary gear carrier 8a and with a first sun gear 9a and with a first flea wheel 10a are in tooth engagement.
  • the planet gears 7a of the first planetary gear set consequently mesh radially between the first sun gear 9a and the first flea wheel 10a.
  • the second planetary gear set 5 has a second planetary gear set with several planetary gears 7b, which are rotatably arranged on a second planetary gear carrier 8b and are in meshing engagement with a second sun gear 9b and with a second flea wheel 10b.
  • the planet gears 7b of the second planetary gear set consequently mesh radially between the second sun gear 9b and the second ring gear 10b. Furthermore, a double clutch device 1 1 with a first clutch 12a and a second clutch 12b is provided. Closing the first clutch 12a and opening the second clutch 12b realizes a first gear ratio, with closing the second clutch 12b and opening the first clutch 12a realizing a second gear ratio. The first gear ratio is not the same as the second gear ratio. By opening both clutches 12a,
  • the torque transmitted from the electric drive machine via the Getriebevor device 3 to the differential stage 6 can be varied between the first and the second gear ratio.
  • the torque transmitted in this way is finally passed on from the differential stage 6 to output shafts 13a, 13b, which are connected, for example, to drive wheels of the motor vehicle.
  • the transmission device 3 thus essentially enables two-speed operation of the motor vehicle.
  • an additional, designed as a spur gear stage Re reducing gear 14 is arranged, which enables an increased spread of the transmission device 3.
  • the first sun gear 9a is non-rotatably connected to the drive shaft 2, which is why the torque of the drive shaft 2 is always introduced into the transmission device 3 via the first sun gear 9a.
  • the first planetary gear carrier 8a is non-rotatably connected to the second sun gear 9b, which in turn is operatively connected to the differential stage 6 via the reduction gear 14.
  • the first ring gear 10a and the second ring gear 10b form a common, one-piece / integral / single-material ring gear with the same toothing.
  • This common ring gear can be fixed in place or connected in a fixed manner to a housing 15 via the second clutch 12b of the dual clutch device 11 fixed to the housing.
  • the first clutch 12a of the double clutch device 11 enables the second planetary gear carrier 8b to be optionally fixed to the housing.
  • the Clutch set the first or second gear ratio and thus the two-speed operation of the transmission device 3 can be realized.
  • Fig. 2 shows a first modification of the drive device 1 according to the invention according to the first embodiment. Only the differences from the drive device 1 according to the first embodiment shown in FIG. 1 will be discussed below.
  • the first modification shown in Fig. 2 represents a drive device 1 in koaxia ler design.
  • the reduction gear 14 is connected on the input side between the electric drive machine and the transmission device 3, in particular the drive shaft 2.
  • the drive shaft 2 is arranged here coaxially to the two output shafts 13a, 13b.
  • FIG. 3 shows a second embodiment of the drive device 1 according to the invention in an axially parallel construction. Only the differences from the drive device 1 shown in FIG. 1 will be discussed below.
  • the first float wheel 10a and the second float wheel 10b do not form a common float wheel, but rather are two separate / separate components.
  • the second flea wheel 10b can accordingly be fixed in place in the housing 15 via the second coupling 12b.
  • the first Flohl wheel 10a is rotatably connected to the second planet carrier 8b, which in turn, as described above, can be connected to the housing via the first clutch 12a.
  • Fig. 4 shows a first modification of the drive device 1 according to the invention according to the second embodiment. Only the differences from the drive device 1 according to the second embodiment shown in FIG. 3 will be discussed below.
  • the first modification of the second embodiment shown in Fig. 4 represents a drive device 1 of coaxial construction. Similar to the drive device shown in Fig. 2, the reduction gear 14 is on the input side between the electric drive machine and the gear device 3, in particular the drive shaft 2, interposed.
  • the drive shaft 2 is arranged here coaxially to the two output shafts 13a, 13b.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

Dispositif d'entraînement (1) pour un véhicule automobile présentant une machine d'entraînement électrique, qui est en liaison active à travers un arbre d'entraînement (2) avec un dispositif de transmission (3), le dispositif de transmission (3) présentant au moins un premier et un deuxième étage d'engrenages planétaires (4, 5) ainsi qu'un étage différentiel (6), le premier étage d'engrenages planétaires (4) présentant un premier train planétaire comprenant plusieurs engrenages planétaires (7a), les engrenages planétaires (7a) du premier train planétaire étant disposés rotatifs sur un premier porte-satellite (8a) et étant en égrènement avec une première roue solaire (9a) ainsi qu'avec une première couronne (10a), le deuxième étage d'engrenages planétaires (5) présentant un deuxième train planétaire comprenant plusieurs engrenages planétaires (7b), les engrenages planétaires (7b) du deuxième train planétaire étant disposés rotatifs sur un deuxième porte-satellite (8b) et étant en engrènement avec une deuxième roue solaire (9b) ainsi qu'avec une deuxième couronne (10b), le premier et le deuxième étage d'engrenages planétaires (4, 5) étant en liaison active avec un dispositif à double couplage (11) comprenant un premier et un deuxième couplage (12a, 12b) commutable sous charge, et le deuxième porte-satellite (8b) pouvant être fixé solidement à un carter (15) à travers le premier couplage (12a) et la deuxième couronne (10b) pouvant être fixé solidement au carter (15) à travers le deuxième couplage (12b).
PCT/DE2020/100625 2019-07-24 2020-07-16 Dispositif d'entraînement pour un véhicule à moteur comprenant au choix un porte-satellite commutable solidaire du boîtier ou une couronne WO2021013301A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019119952.2A DE102019119952B4 (de) 2019-07-24 2019-07-24 Antriebsvorrichtung für ein Kraftfahrzeug mit wahlweise gehäusefest schaltbarem Planetenradträger oder Hohlrad
DE102019119952.2 2019-07-24

Publications (1)

Publication Number Publication Date
WO2021013301A1 true WO2021013301A1 (fr) 2021-01-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2020/100625 WO2021013301A1 (fr) 2019-07-24 2020-07-16 Dispositif d'entraînement pour un véhicule à moteur comprenant au choix un porte-satellite commutable solidaire du boîtier ou une couronne

Country Status (2)

Country Link
DE (1) DE102019119952B4 (fr)
WO (1) WO2021013301A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4075023B1 (fr) 2021-04-16 2023-12-27 Volvo Construction Equipment AB Agencement de transmission
EP4075021B1 (fr) 2021-04-16 2023-10-18 Volvo Construction Equipment AB Agencement de transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008041887A1 (de) * 2008-09-09 2010-03-11 Zf Friedrichshafen Ag Hybridantriebsstrang eines Kraftfahrzeugs
WO2014029650A1 (fr) * 2012-08-24 2014-02-27 Avl List Gmbh Unité d'entraînement
DE102014215156A1 (de) * 2014-08-01 2016-02-04 Zf Friedrichshafen Ag Gruppengetriebe eines Kraftfahrzeugs
WO2019007723A1 (fr) * 2017-07-01 2019-01-10 Daimler Ag Dispositif de transmission pour un entraînement électrique d'un véhicule à moteur, et entraînement électrique pour un véhicule à moteur

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011088668B4 (de) * 2011-12-15 2019-05-09 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung mit einer elektrischen Maschine
DE102013220068A1 (de) * 2013-10-02 2015-04-02 Schaeffler Technologies Gmbh & Co. Kg Getriebevorrichtung mit einem CVT-Getriebe und mit einem Differenzial
DE102013225519A1 (de) * 2013-12-11 2015-06-11 Bayerische Motoren Werke Aktiengesellschaft Planetenradgetriebe und Antriebseinheit, insbesondere für Elektrofahrzeuge
US11028906B2 (en) * 2017-11-17 2021-06-08 Aisin Aw Co., Ltd. Vehicle drive system
DE102019107517B3 (de) * 2019-03-25 2020-07-23 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008041887A1 (de) * 2008-09-09 2010-03-11 Zf Friedrichshafen Ag Hybridantriebsstrang eines Kraftfahrzeugs
WO2014029650A1 (fr) * 2012-08-24 2014-02-27 Avl List Gmbh Unité d'entraînement
DE102014215156A1 (de) * 2014-08-01 2016-02-04 Zf Friedrichshafen Ag Gruppengetriebe eines Kraftfahrzeugs
WO2019007723A1 (fr) * 2017-07-01 2019-01-10 Daimler Ag Dispositif de transmission pour un entraînement électrique d'un véhicule à moteur, et entraînement électrique pour un véhicule à moteur

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DE102019119952B4 (de) 2021-07-22

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