DE102016202723B4 - High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle - Google Patents
High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle Download PDFInfo
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- DE102016202723B4 DE102016202723B4 DE102016202723.9A DE102016202723A DE102016202723B4 DE 102016202723 B4 DE102016202723 B4 DE 102016202723B4 DE 102016202723 A DE102016202723 A DE 102016202723A DE 102016202723 B4 DE102016202723 B4 DE 102016202723B4
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- 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
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- 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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- 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
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
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- 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
- F16H2003/447—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the set of orbital gears and the output
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- 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
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
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- 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
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- 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
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- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
Abstract
Umlaufräderschaltgetriebe mit: – einem Leistungseingang (I1), – einem Leistungsausgang (O1), – einem Vorstufengetriebe (VG), das durch den Leistungseingang (I1) getrieben wird, mit einem festen Übersetzungsverhältnis mit einem Vorstufensonnenrad (VS1), einem Vorstufenplanetensatz (VP1), einem Vorstufenplanetenträger (VC1) und einem Vorstufenhohlrad (VH1), – einem Laststufengetriebe (LG), das durch das Vorstufengetriebe (VG) getrieben wird, mit einem ersten Laststufensonnenrad (LS1), einem zweiten Laststufensonnenrad (LS2), Laststufenplaneten (LP1, LP2), einem ersten Laststufenplanetenträger (LC1) und einem ersten Laststufenhohlrad (LH1), und – einer Doppelkupplungseinrichtung (DK), mit einer ersten Kupplung (K1) und einer zweiten Kupplung (K2), die in einem räumlich axial zwischen dem Vorstufengetriebe (VG) und dem Laststufengetriebe (LG) liegenden Zwischenbereich angeordnet ist, wobei – der Leistungsabgriff aus dem Laststufengetriebe (LG) über den Laststufenplanetenträger (LC1) erfolgt, und – die Planeten des ersten Laststufenplanetensatzes (LP1) radial von innen her in das Laststufenhohlrad (LH1) eingreifen, dadurch gekennzeichnet, dass – die erste Kupplung (K1) der selektiven Ankoppelung des ersten Laststufensonnenrades (LS1) an den Vorstufenplanetenträger (VC1) dient, – die zweite Kupplung (K2), der selektiven Ankoppelung des zweiten Laststufensonnenrades (LS2) an den Vorstufenplanetenträger (VC1) dient, – der erste Laststufenplanetensatz (LP1) und der zweite Laststufenplanetensatz (LP2) gemeinsam einen Stufenplanetensatz mit gestuften Planeten bilden, – das erste Laststufenhohlrad (LH1) an einem Getriebegehäuse (G) des Umlaufräderschaltgetriebes stationär festgelegt ist.Epicyclic gearbox comprising: - a power input (I1), - a power output (O1), - a precursor transmission (VG) driven by the power input (I1), a fixed gear ratio with a pre-stage sun gear (VS1), a pre-stage planetary gearset (VP1) a precursor planet carrier (VC1) and a precursor ring gear (VH1), a load stage transmission (LG) driven by the precursor transmission (VG), a first load stage sun gear (LS1), a second load stage sun gear (LS2), on-load planetary gears (LP1, LP2 ), a first on-load planetary carrier (LC1) and a first load stage ring gear (LH1), and - a dual clutch device (DK), with a first clutch (K1) and a second clutch (K2), which in a spatially axially between the precursor transmission (VG) and the load stage transmission (LG) lying intermediate region is arranged, wherein - the power tap from the load stage transmission (LG) on the Laststufenplaneten carrier (LC1) takes place, and - the planets of the first on-load planetary gear set (LP1) engage radially from the inside in the Laststufenhohlrad (LH1), characterized in that - the first clutch (K1) of the selective coupling of the first Laststufensonnenrades (LS1) to the Pre-stage planet carrier (VC1) serves - the second clutch (K2), which selectively couples the second load stage sun gear (LS2) to the pre-stage planet carrier (VC1), - the first on-load planetary set (LP1) and the second on-load planetary set (LP2) share a stepped planetary set with staged ones Form planet, - the first load stage ring gear (LH1) is fixed to a transmission housing (G) of the epicyclic gearbox stationary.
Description
Gebiet der ErfindungField of the invention
Die Erfindung bezieht sich auf ein Umlaufräderschaltgetriebe gemäß dem Oberbegriff von Patentanspruch 1.The invention relates to a planetary gearbox according to the preamble of claim 1.
Aus
Aus
Aufgabe der ErfindungObject of the invention
Der Erfindung liegt die Aufgabe zugrunde, ein Umlaufräderschaltgetriebe mit hoher Gesamtübersetzungswirkung zu schaffen, das sich durch einen hohen mechanischen Wirkungsgrad auszeichnet.The invention has for its object to provide a planetary gearbox with high overall transmission efficiency, which is characterized by a high mechanical efficiency.
Erfindungsgemäße LösungInventive solution
Diese Aufgabe wird erfindungsgemäß durch ein Umlaufräderschaltgetriebe mit den in Patentanspruch 1 angegebenen Merkmalen gelöst.This object is achieved by a planetary gear with the features specified in claim 1.
Dadurch wird es auf vorteilhafte Weise möglich, ein Umlaufräderschaltgetriebe zu schaffen, bei welchem eine als Doppelkupplung ausgebildete Kupplungsmechanik in einem Getriebeabschnitt wirksam ist, in welchem bereits eine mittlere Drehmomentenerhöhung sowie entsprechend eine mittlere Drehzahlabsenkung vorliegt.This advantageously makes it possible to provide a epicyclic gearbox in which a clutch mechanism designed as a double clutch is effective in a transmission section in which there is already an average torque increase and, correspondingly, an average speed reduction.
Die in das Laststufenhohlrad radial von innen her eingreifenden Planeten des ersten Laststufenplanetensatzes weisen vorzugsweise einen Teilkreisdurchmesser auf, der kleiner ist als der Teilkreisdurchmesser der Planeten des zweiten Laststufenplanetensatzes.The radially engaging from the inside in the Laststufenhohlrad planets of the first load stage planetary set preferably have a pitch circle diameter which is smaller than the pitch circle diameter of the planets of the second load stage planetary set.
Das erfindungsgemäße Umlaufräderschaltgetriebe kann in vorteilhafter Weise derart aufgebaut werden, dass dieses einen Wellenzapfen umfasst, welcher das erste Laststufensonnenrad mit einem Innenläufer der ersten Kupplung verbindet, wobei auf diesem Wellenzapfen eine Hohlwelle drehbar angeordnet ist, welche das zweite Laststufensonnenrad mit einem Innenläufer der zweiten Kupplung verbindet. Zwischen dieser Hohlwelle und dem Wellenzapfen kann ein Gleit- oder vorzugsweise ein Wälzlager vorgesehen sein, das eine radiale Abstützung der beiden Komponenten aneinander ermöglicht.The epicyclic gearbox according to the invention can be advantageously constructed such that this comprises a shaft journal which connects the first Laststufensonnenrad with an inner rotor of the first clutch, wherein on this shaft journal a hollow shaft is rotatably arranged, which connects the second Laststufensonnenrad with an inner rotor of the second clutch , Between this hollow shaft and the shaft journal, a sliding or preferably a roller bearing can be provided, which allows a radial support of the two components together.
Das zweite Laststufensonnenrad ist der ihm zugeordneten zweiten Kupplung enger benachbart als das erste Laststufenrad der diesem zugeordneten ersten Kupplung. Durch diese spezielle Schachtelung ergibt sich eine vorteilhafte Belastung des Laststufenplanetenträgers und eine Reduzierung der radialen Getriebeabmessungen, da das Laststufenhohlrad radial unter den zur Getriebeachse konzentrischen Umlaufhüllkreis der Planeten des zweiten Laststufenplanetensatzes eintaucht und damit einen kleineren Durchmesser aufweist, als wenn dieses mit den Planeten des zweiten Laststufenplanetensatzes gepaart werden würde. Auch liegt das erste Laststufenhohlrad näher am Getriebeausgang.The second load stage sun gear is closer to the second clutch associated therewith than the first load stage gear of the first clutch associated therewith. This special nesting results in an advantageous loading of the load stage planet carrier and a reduction of the radial transmission dimensions, since the load stage ring gear dips radially under the concentric to the transmission axis Umlaufhüllkreis the planet of the second load stage planetary set and thus has a smaller diameter than if this with the planet of the second load stage planetary set would be paired. Also, the first load stage ring gear is closer to the transmission output.
Die beiden Kupplungen der Doppelkupplungseinrichtung sind vorzugsweise als Lamellenkupplungen ausgebildet, deren Lamellen wechselweise am entsprechenden Innenläufer und am Kupplungsgehäuse drehfest, jedoch axial verschiebbar geführt sind. Jenes Kupplungsgehäuse kann dabei unmittelbar drehstarr an den Planetenträger der Vorstufe angebunden sein. Die Kupplungen der Doppelkupplung sind vorzugsweise axial nebeneinander liegend angeordnet und vorzugsweise durch Einsatz möglichst vieler gleichartiger Bauteile realisiert.The two clutches of the dual clutch device are preferably designed as multi-plate clutches, the lamellae alternately rotatably on the corresponding inner rotor and the clutch housing, but are guided axially displaceable. That clutch housing can be directly connected torsionally rigidly to the planet carrier of the preliminary stage. The clutches of the double clutch are preferably arranged axially next to one another and are preferably realized by using as many identical components as possible.
Das erfindungsgemäße Umlaufräderschaltgetriebe kann weiterhin in vorteilhafter Weise derart aufgebaut sein, dass der Wellenzapfen zum Antrieb des ersten Sonnenrades und eine das Vorstufensonnenrad treibende Eingangswelle aneinander zentriert sind.The epicyclic gearbox according to the invention can also be constructed in an advantageous manner such that the shaft journal for driving the first sun gear and an input shaft driving the pre-stage sun gear are centered on each other.
Mit dem erfindungsgemäßen Getriebe können in besonders vorteilhafter Weise zwei Gänge im Bereich von i = 15 und i = 7,5 realisiert werden, wobei eine Welle der einfachen Vorstufe mit der jeweils anderen Welle der ausgangsseitigen Überlagerungsgetriebestufe verbunden werden muss. Dies wird erfindungsgemäß mittels einer Doppelkupplung bewerkstelligt, deren Kupplungskorb immer mit dem Steg, d. h. dem Planetenträger der Vorstufe verbunden ist. Die als Laststufe fungierende Überlagerungsgetriebestufe ist vorzugsweise als Koppelgetriebe mit gestuften Planeten ausgeführt. Die Doppelkupplung sitzt axial zwischen der Vorstufe und der die Schaltfunktion bietenden Überlagerungsgetriebestufe.With the transmission according to the invention, two gears in the range of i = 15 and i = 7.5 can be realized in a particularly advantageous manner, with one shaft of the simple precursor having to be connected to the respective other shaft of the output-side superposition gear stage. This is accomplished according to the invention by means of a double clutch whose clutch basket always with the web, d. H. connected to the planet carrier of the preliminary stage. The acting as a load stage superposition gear stage is preferably designed as a coupling gear with stepped planet. The dual clutch is located axially between the pre-stage and the shift function bidding superposition gear.
Kurzbeschreibung der Figuren Brief description of the figures
Weitere Einzelheiten und Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung in Verbindung mit der Zeichnung. Es zeigt:Further details and features of the invention will become apparent from the following description taken in conjunction with the drawings. It shows:
Ausführliche Beschreibung der FigurenDetailed description of the figures
Die Darstellung nach
Weiterhin umfasst das erfindungsgemäße Umlaufräderschaltgetriebe ein Laststufengetriebe LG, das durch das Vorstufengetriebe VG getrieben wird, mit einem ersten Laststufensonnenrad LS1, einem zweiten Laststufensonnenrad LS2, einem ersten Laststufenplanetensatz LP1, einem zweiten Laststufenplanetensatz LP2, einem ersten Laststufenplanetenträger LC1 und einem ersten Laststufenhohlrad LH1.Furthermore, the epicyclic gearbox according to the invention comprises a power-shift transmission LG, which is driven by the precursor transmission VG, with a first load stage sun gear LS1, a second load stage sun gear LS2, a first on-load planetary set LP1, a second on-load planetary set LP2, a first on-stage planet carrier LC1 and a first on-load stage ring gear LH1.
Das erfindungsgemäße Umlaufräderschaltgetriebe zeichnet sich dadurch aus, dass dieses eine Doppelkupplungseinrichtung DK umfasst, mit einer ersten Kupplung K1, zur selektiven Ankoppelung des ersten Laststufensonnenrades LS1 an den Vorstufenplanetenträger VC1, und einer zweiten Kupplung K2, zur selektiven Ankoppelung des zweiten Laststufensonnenrades LS2 an den Vorstufenplanetenträger VC1, wobei die Doppelkupplungseinrichtung DK in einem räumlich axial zwischen dem Vorstufengetriebe VG und dem Laststufengetriebe LG liegenden Zwischenbereich angeordnet ist.The epicyclic gearbox according to the invention is characterized in that it comprises a dual clutch device DK, with a first clutch K1, for selective coupling of the first Laststufensonnenrades LS1 to the Vorstufenplanetenträger VC1, and a second clutch K2, for selectively coupling the second Laststufensonnenrades LS2 to the Vorstufenplanetenträger VC1 wherein the dual clutch device DK is arranged in an intermediate region lying spatially axially between the pre-stage transmission VG and the load-stage transmission LG.
Durch den beschriebenen Aufbau wird es möglich, ein Umlaufräderschaltgetriebe zu schaffen, bei welchem eine als Doppelkupplung ausgebildete Kupplungsmechanik DK in einem Getriebeabschnitt wirksam ist, in welchem bereits eine mittlere Drehmomentenerhöhung sowie entsprechend eine mittlere Drehzahlabsenkung vorliegt.By the described construction, it becomes possible to provide a planetary gear, in which a designed as a double clutch clutch mechanism DK is effective in a transmission section in which there is already an average torque increase and correspondingly an average speed reduction.
Durch die Anbindung der Doppelkupplungseinrichtung an den Vorstufenplanetenträger VC1 wird erreicht, dass der Leistungseingang I1, das Vorstufensonnenrad VS1, der Vorstufenplanetenträger VC1 und die beiden Laststufensonnenräder LS1, LS2 sowie auch der Laststufenplanetenträger LC1 mit dem gleichen Drehsinn rotieren, so dass sich im Innenbereich keine gegenläufigen Schmierstoffwirbel ergeben. Das erfindungsgemäße Umlaufräderschaltgetriebe zeichnet sich damit auch durch einen hohen mechanischen Wirkungsgrad aus.The connection of the dual clutch device to the precursor planet carrier VC1 ensures that the power input I1, the pre-stage sun gear VS1, the precursor planet carrier VC1 and the two load stage sun gears LS1, LS2 as well as the load stage planet carrier LC1 rotate with the same sense of rotation, so that there are no opposing lubricant swirls in the interior result. The epicyclic gearbox according to the invention is thus characterized by a high mechanical efficiency.
Der Leistungsabgriff aus dem Laststufengetriebe LG erfolgt bei dem dargestellten Ausführungsbeispiel über den Laststufenplanetenträger LC1. Die Planeten des ersten Laststufenplanetensatzes LP1 greifen radial von innen her in das Laststufenhohlrad LH1 ein. Der erste Laststufenplanetensatz LP1 und der zweite Laststufenplanetensatz LP2 bilden gemeinsam einen aus Stufenplaneten bestehenden Stufenplanetensatz. Die in das Laststufenhohlrad LH1 eingreifenden Planeten des ersten Laststufenplanetensatzes LP1 weisen dabei einen Teilkreisdurchmesser auf, der kleiner ist als der Teilkreisdurchmesser der Planeten des zweiten Laststufenplanetensatzes LP2. Jeweils ein Planet des ersten Planetensatzes LP1 ist mit einem Planeten des zweiten Planetensatzes LP2 drehstarr verbunden. Die so gebildeten Stufenplaneten sind auf Planetenbolzen drehbar gelagert, die in dem zur Bewerkstelligung des Leistungsabgriffs vorgesehene Laststufenplanetenträger LC1 verankert sind.The power tap from the load stage transmission LG takes place in the illustrated embodiment via the load stage planet carrier LC1. The planets of the first load stage planetary set LP1 engage radially from the inside into the load stage ring gear LH1. The first on-load planetary set LP1 and the second on-load planetary set LP2 together form a step planetary set consisting of stepped planets. The engaging in the Laststufenhohlrad LH1 planets of the first load stage planetary set LP1 in this case have a pitch circle diameter which is smaller than the pitch circle diameter of the planets of the second load stage planetary set LP2. In each case one planet of the first planetary set LP1 is rotationally rigidly connected to a planet of the second planetary set LP2. The stepped planets thus formed are rotatably mounted on planetary pins which are anchored in the load stage planetary carrier LC1 provided for effecting the power tap.
Das erfindungsgemäße Umlaufräderschaltgetriebe umfasst einen Wellenzapfen LW1, welcher das erste Laststufensonnenrad LS1 mit einem Innenläufer BK1 der ersten Kupplung K1 verbindet. Auf diesem Wellenzapfen LW1 ist eine Hohlwelle LW2 drehbar angeordnet, welche das zweite Laststufensonnenrad LS2 mit dem Innenläufer BK2 der zweiten Kupplung K2 verbindet.The epicyclic gearbox according to the invention comprises a shaft journal LW1 which connects the first load stage sun gear LS1 to an internal rotor BK1 of the first clutch K1. On this shaft journal LW1 a hollow shaft LW2 is rotatably arranged, which connects the second Laststufensonnenrad LS2 with the inner rotor BK2 of the second clutch K2.
Die beiden Kupplungen K1, K2 sind als Lamellenkupplungen ausgebildet, wobei die Doppelkupplung DK ein Kupplungsgehäuse DK1 aufweist, das drehstarr an den Planetenträger VC1 der Vorstufe VS angebunden ist. Die Kupplungen K1, K2 der Doppelkupplung DK sind axial nebeneinander liegend angeordnet und durch Einsatz gleichartiger Bauteile realisiert.The two clutches K1, K2 are formed as multi-plate clutches, wherein the dual clutch DK has a clutch housing DK1, which is rotationally rigidly connected to the planet carrier VC1 of the precursor VS. The clutches K1, K2 of the double clutch DK are arranged axially next to each other and realized by using similar components.
Das oben beschriebene Getriebe kann so ausgelegt werden, dass sich die Übersetzungsverhältnisse im jeweiligen Schaltzustand um einen Faktor im Bereich von 1,4 bis 2,4 unterscheiden, und zudem eine maximale Übersetzung im Bereich von 11 bis 17, insbesondere 15 realisierbar ist.The transmission described above can be designed so that the gear ratios differ in the respective switching state by a factor in the range of 1.4 to 2.4, and also a maximum ratio in the range of 11 to 17, in particular 15 can be realized.
Der Antrieb des ersten Vorstufensonnenrades LS1 kann durch einen elektromechanischen Hauptantriebsmotor bewerkstelligt werden, indem das erste Vorstufensonnenrad VS1 unmittelbar auf einer Rotorwelle dieses Motors sitzt. Der Motor und das beschriebene erfindungsgemäße Getriebe können zu einer Baueinheit zusammengefasst werden.The drive of the first pre-stage sun gear LS1 can be accomplished by a main electromechanical drive motor by having the first pre-stage sun gear VS1 directly seated on a rotor shaft of that motor. The engine and the described transmission according to the invention can be combined to form a structural unit.
Die Betätigung der Doppelkupplung DK erfolgt vorzugsweise unter Einsatz elektromechanischer Aktuatoren. Die Ansteuerung dieser Aktuatoren erfolgt vorzugsweise über eine elektronische Steuereinrichtung, die im Rahmen eines Schaltvorgangs auch die Leistung des Antriebsmotors so dosiert, dass ein möglichst ruckfreier Schaltvorgang erreicht wird.The actuation of the double clutch DK is preferably carried out using electromechanical actuators. The actuation of these actuators is preferably carried out via an electronic control device which also doses the power of the drive motor in the context of a switching operation so that the smoothest possible switching operation is achieved.
Claims (7)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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DE102018128774A1 (en) | 2018-11-16 | 2020-05-20 | Schaeffler Technologies AG & Co. KG | Planetary gear with two gears and drive unit |
DE102018129174A1 (en) | 2018-11-20 | 2020-05-20 | Schaeffler Technologies AG & Co. KG | Two-stage planetary gear and drive unit |
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CN107100965A (en) | 2017-08-29 |
CN107100965B (en) | 2022-06-03 |
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