WO2003025431A1 - Automatic multi-speed vehicle gearbox - Google Patents

Automatic multi-speed vehicle gearbox Download PDF

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Publication number
WO2003025431A1
WO2003025431A1 PCT/EP2002/009623 EP0209623W WO03025431A1 WO 2003025431 A1 WO2003025431 A1 WO 2003025431A1 EP 0209623 W EP0209623 W EP 0209623W WO 03025431 A1 WO03025431 A1 WO 03025431A1
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WO
WIPO (PCT)
Prior art keywords
gear
speed vehicle
vehicle transmission
transmission according
automated multi
Prior art date
Application number
PCT/EP2002/009623
Other languages
German (de)
French (fr)
Inventor
Wolfgang Rieger
Gerhard Gumpoltsberger
Jürgen WAFZIG
Detlef Baasch
Ralf Dreibholz
Markus Knobelspies
Original Assignee
Zf Friedrichshafen Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2003025431A1 publication Critical patent/WO2003025431A1/en

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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
    • 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
    • F16H37/0833—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 arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—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 arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • 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
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
    • 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
    • F16H37/0833—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 arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths

Definitions

  • the invention relates to an automated multi-speed vehicle transmission, in which a plurality of power paths are provided between an input shaft and an output shaft for shifting the gears, which are summed in a planetary gear summing gear, the ratio being variable in at least one of the power paths.
  • Automated manual transmissions which are generally known from practice, are based predominantly on the principle of conventional manual transmissions in countershaft construction, in which a shift is implemented with the aid of synchronizations.
  • Such transmissions have relatively small shift elements, but the performance-determining elements, such as spur gear stages, require a large installation space and are also cost-intensive.
  • Gearbox types are known from practice which try to take advantage of the countershaft gearbox the small shifting elements and the advantages of the powershift automatic transmission with planetary gear sets with regard to the compact gears, by providing a planetary gear shift set in a countershaft transmission, in which case there is a group transmission with a purely geometrical gradation.
  • One problem here is that the gradation is very low in lower gears, while it is very large in higher gears, which makes driving more difficult for passenger cars.
  • Another known transmission design is represented by so-called power split transmissions or multi-range transmissions, which can realize many driving ranges with just a few shift elements.
  • a combination of features of the transmission types described above shows a transmission described in US Pat. No. 5,013,289, which has a countershaft transmission area and two planetary gears. Three power paths are provided between a transmission input shaft and an output which is not arranged coaxially for this purpose, in which the gear ratio can be changed by means of a load shift. By providing three power paths that can be connected to the planetary gear sets, six forward gears can be realized with a relatively small number of switching elements.
  • a multi-speed vehicle transmission of the type mentioned at the outset, in which at least one gear ratio is switched positively, offers the advantage that it has a significantly simpler and more cost-effective construction than planetary powershift transmissions, since at least some of the complex hydraulic systems for the shifting elements are dispensed with can. Due to the lack of or at least less use of hydraulics with the associated drag losses, better efficiency is achieved.
  • a multi-speed vehicle transmission as a six-speed transmission, e.g. Two power de can be provided, the planetary gear summing gear being designed as a three-shaft gear with a simple planetary gear.
  • a transmission is e.g. Realizable with four countershaft levels instead of seven countershaft levels and only six instead of seven synchronizations.
  • the multi-speed vehicle transmission according to the invention can be equipped in an advantageous embodiment with three performance paths, the planetary gear set summing gear being designed as a four-shaft gear unit with a double planetary gear set. Two wheel planes and five synchronizations are sufficient to implement six forward gears.
  • more than three power paths can also be provided, the planetary gear summing gear then being constructed from at least four shafts.
  • the translations in the individual performance paths can also be the same, it is usually still expedient if the performance paths have different translations.
  • the translation must be changeable in at least one of the performance paths.
  • the translations are not continuously variable. riabel, but designed as spur gear ratios or as a direct connection, preferably all of which are positively connected by synchronizations or claw couplings, each of which connects two shafts or a shaft and a housing.
  • the arrangement of the switching elements is preferably selected so that the synchronizations or claw clutches are combined into pairs and can be switched as synchronous or claw packets with a power actuation, i.e. that, for example, in an advantageous embodiment, two dog clutches can be actuated by a shift fork, only one or none of the dog clutches being actuated in each case.
  • Fig.l is a schematic diagram of a first variant of an automated multi-speed
  • the summing gear has a simple planetary gear set
  • 2a shows a transmission diagram of an exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention
  • FIG. 2b shows a switching logic belonging to the transmission diagram according to FIG. 2a;
  • FIG. 3a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention
  • FIG. 3b shows a switching logic belonging to the transmission diagram according to FIG. 3a;
  • FIG. 4a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention.
  • FIG. 4b shows a switching logic belonging to the transmission diagram according to FIG. 4a
  • FIG. 5 shows a basic diagram of a second variant of a multi-speed vehicle transmission according to the invention, the summation transmission of which has a double planetary gear set;
  • 6a shows a transmission diagram of an exemplary embodiment of the multi-speed vehicle transmission according to the second variant according to FIG. 4;
  • FIG. 6b shows a switching logic belonging to the transmission diagram according to FIG. 6a
  • 7a shows a transmission diagram of a second exemplary embodiment of a multi-speed vehicle transmission according to the second variant according to FIG. 4
  • FIG. 7b shows a shifting logic belonging to the transmission scheme according to FIG. 7a.
  • FIG. 1 shows a basic diagram of a first variant of an automated multi-speed vehicle transmission 1, which in the present case has six forward gears and one reverse gear.
  • the vehicle transmission 1 has, between an input shaft or drive shaft 2 and an output shaft 3 connected to an output, a countershaft transmission 4 and a planetary gear summing gear 5, which in the present case is a differential and is designed as a three-shaft gear with a simple planetary gear set.
  • the power of the input shaft 2 can be divided into two power paths P1, P2, a first power path P1 being connected to a first shaft 6 and a second power path P2 being connected to a second shaft 7 of the three-shaft transmission 5.
  • the third shaft of the three-shaft gear 5 represents the output shaft 3 connected to the output.
  • translation stages il, i2 and i3 are provided, which are preferably designed in the countershaft design.
  • first power path P1 two fixed translations i1, i2 arranged in parallel are provided, which can be connected via assigned clutches K1 or K2.
  • second power path P2 Translation ⁇ 3 is also a fixed one in the second power path P2 Translation ⁇ 3 provided that can be switched into the power flow via an associated clutch K3.
  • a reverse gear can be achieved either by an additional spur gear stage with integrated speed reversal or by a speed reversal in the planetary gear set.
  • FIGS. 2a and 2b show a transmission and shifting diagram of such an automated multi-speed vehicle transmission.
  • six shifting elements or clutches A, B, C, D, E and F that are to be switched as well as a planetary gear summing gear 5 designed as a three-shaft gear are provided.
  • a reverse gear 8 is also provided between the clutch C and the countershaft 9.
  • the gearshifts are made via synchronizers 39 or dog clutches.
  • the planetary gear set summing gear 5 is a simple planetary gear set, which has planet gears 12 that roll between a sun gear 10 and a ring gear 11, the planet gear carriers of which are firmly connected to the output shaft 3 leading to the output.
  • the gear step is progressive, ie that the Jump of the ratio i between the gears with increasing number of gears becomes less and less.
  • FIGS. 3a and 3b show a transmission diagram essentially corresponding to the embodiment according to FIGS. 2a and 2b, with associated shift logic, with a greater spread of the transmission here due to the design of the planetary gear summing transmission 5 with between a sun gear 13 and a with the output shaft 3 fixedly connected ring gear 14 radially adjacent planet gears 15, 16 which are mounted on a common planet carrier 17 is achieved.
  • FIGS. 4a and 4b show a further variant of the gear shift with the associated shift logic, which essentially corresponds to the embodiment according to FIGS. 2a and 2b as well as FIGS. 3a and 3b, which is why the analog gear components are not further discussed here is received.
  • the reverse gear is not realized by a spur gear stage with an intermediate gear as in the embodiment according to FIGS. 2a and 3a, but by a reversal of the direction of rotation in the planetary gear set of the planetary gear set 5.
  • Such a reversal of the direction of rotation is achieved by holding and supporting a ring gear 53 Planet set reached by means of the switching element A on a housing 40 of the transmission.
  • FIG. 5 shows a schematic diagram of a second variant of an automated six-speed vehicle transmission 1.
  • the power of the input shaft 2 can be separated into three power paths P10, P20 and P30, which via corresponding input shafts 18, 19, 20 Planet gear summing gear 50 mouth, which is designed here as a double differential in the form of a four-shaft gear with a double planetary gear.
  • three performance paths P10, P20 and P30 with the respective assigned ratios ilO, i20, i30 and clutches K10, K20, K30 as well as two shift elements or brakes Bl and B2 supported on the transmission housing, six forward gears and one reverse gear can be carried out.
  • Two of the three power paths P10, P20 and P30 are combined in the planetary gear summing gear 5.
  • an additional clutch can also be provided between two of the power paths.
  • FIGS. 6a and 6b An exemplary embodiment of such a variant of a multi-speed vehicle transmission is shown in FIGS. 6a and 6b, which for shifting six forward gears five shifting elements A, B, C, D, E to be switched and a planetary gear summing gear 50 which represents a four-shaft transmission with two planetary gear sets.
  • the planetary gear summing gear 50 here consists of a common ring gear 21, which is fixedly connected to the output shaft 3 leading to the output, two sun gears 22, 23 of different sizes, and planet gears 24, 25 of different lengths which roll between them and the ring gear 21 and which have a common length Have planet carrier 26.
  • the planetary gear summing gear 50 thus essentially corresponds to a known Ravigneaux gear.
  • connection to the countershaft 27 is established via two wheel planes 28, 29.
  • 7a and 7b show a further exemplary embodiment of the second variant of an automated multi-speed vehicle transmission according to the invention, in which the planetary gear summing gear 50 is a typical four-shaft set with a common sun gear 30, two ring gears
  • the output shaft 3 is connected to one of the planet carriers 34.
  • the planetary gear summing gear 50 is arranged in the power train between the all form-fitting shifting elements A, E, C on the one hand and B, F on the other hand, the planetary gear arrangement being simpler to build, because the lateral forces of the spur gear stages are supported close to the housing.
  • the countershaft 35 can be connected to the input shaft 2 and the shifting elements via three wheel planes 36, 37, 38.
  • the gear ratio is designed progressively both in the embodiment according to FIGS. 6a and 6b and in the embodiment according to FIGS. 7a and 7b.
  • the multi-speed vehicle transmission according to the invention is of course not limited to the designs shown as a six-speed vehicle transmission, but is also suitable for transmissions with a different, in particular higher number of gears.
  • the arrangement of the individual elements in the exemplary embodiments shown is also not mandatory, since, for example, the planetary gear summation gear, as already shown in the embodiment according to FIG. 6, can be arranged at different points between the input shaft and the output shaft of the vehicle transmission.
  • each gear ratio is switched positively, it can also be provided that non-positive or frictional shifting elements are used in addition to the positively locking shifting elements.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention relates to an automatic multi-speed vehicle gearbox. To select the gears in said gearbox several output paths, which are summarised in a planetary gear set summarising gear, are provided between an input shaft and an output shaft. According to the invention, the ratio change is stepped in at least one of the output paths. In addition, at least one ratio is selected by a positive engagement.

Description

Automatisiertes Mehrgang-Fahrzeuggetriebe Automated multi-speed vehicle transmission
Die Erfindung betrifft ein automatisiertes Mehrgang- Fahrzeuggetriebe, bei dem zwischen einer Eingangswelle und einer Ausgangswelle zur Schaltung der Gange mehrere Leistungspfade vorgesehen sind, die in einem Planetensatz- Summiergetriebe summiert werden, wobei in wenigstens einem der Leistungspfade die Übersetzung gestuft veränderbar ist.The invention relates to an automated multi-speed vehicle transmission, in which a plurality of power paths are provided between an input shaft and an output shaft for shifting the gears, which are summed in a planetary gear summing gear, the ratio being variable in at least one of the power paths.
Automatisierte Schaltgetriebe, welche allgemein aus der Praxis bekannt sind, basieren vorwiegend auf dem Prinzip herkömmlicher Handschaltgetriebe in Vorgelegebauweise, bei denen eine Schaltung mit Hilfe von Synchronisierungen realisiert wird. Solche Getriebe weisen verhältnismäßig kleine Schaltelemente auf, jedoch benotigen die leistungsbestimmenden Elemente, wie Stirnradstufen, einen großen Bauraum und sind zudem kostenintensiv.Automated manual transmissions, which are generally known from practice, are based predominantly on the principle of conventional manual transmissions in countershaft construction, in which a shift is implemented with the aid of synchronizations. Such transmissions have relatively small shift elements, but the performance-determining elements, such as spur gear stages, require a large installation space and are also cost-intensive.
Hinsichtlich ihres Aufbaus wesentlich kompakter sind aus der Praxis bekannte Lastschaltautomatgetriebe mit Pla- netensatzen gestaltet, welche eine interne Leistungsverzweigung aufweisen können. Wenngleich diese Getriebe aufgrund ihrer kompakten Bauweise einen relativ geringen Bauraum beanspruchen, so ist bei dieser Getriebeart jedoch nachteilig, daß die Schaltelemente, wie Kupplungen und Bremsen, verhältnismäßig groß dimensioniert und hydraulisch betätigt werden müssen. Daraus ergeben sich erhebliche Schleppverluste und eine entsprechend große Betatigungs- energie, was sich negativ auf den Wirkungsgrad des Getriebes auswirkt.With regard to their construction, they are designed to be significantly more compact, known from practice, automatic power shift transmissions with planetary gear sets, which can have an internal power split. Although these gearboxes require a relatively small amount of space due to their compact design, it is disadvantageous in this type of gearbox that the switching elements, such as clutches and brakes, have to be of relatively large dimensions and actuated hydraulically. This results in considerable drag losses and a correspondingly large actuation energy, which has a negative effect on the efficiency of the transmission.
Es sind aus der Praxis Getriebetypen bekannt, welche versuchen, die Vorteile der Vorgelegegetriebe hinsichtlich der kleinen Schaltelemente und die Vorteile der Lastschaltautomatikgetriebe mit Planetensatzen hinsichtlich der kompakten Verzahnungen miteinander zu verbinden, indem bei einem Vorgelegegetriebe ein Planetennachschaltsatz vorgesehen wird, wobei dann ein Gruppengetriebe mit rein geometrischer Stufung vorliegt. Problematisch ist hierbei u.a., daß die Stufung bei niedrigeren Gangen sehr gering ist, wahrend sie bei höheren Gangen sehr groß ist, was die Fahrbarkeit für Personenkraftwagen erschwert.Gearbox types are known from practice which try to take advantage of the countershaft gearbox the small shifting elements and the advantages of the powershift automatic transmission with planetary gear sets with regard to the compact gears, by providing a planetary gear shift set in a countershaft transmission, in which case there is a group transmission with a purely geometrical gradation. One problem here is that the gradation is very low in lower gears, while it is very large in higher gears, which makes driving more difficult for passenger cars.
Eine andere bekannte Getriebebauform stellen sogenannte Leistungsverzweigungsgetriebe bzw. Mehrbereichsgetriebe dar, welche mit wenigen Schaltelementen viele Fahrbereiche realisieren können.Another known transmission design is represented by so-called power split transmissions or multi-range transmissions, which can realize many driving ranges with just a few shift elements.
Eine Kombination von Merkmalen der vorbeschriebenen Getriebetypen zeigt ein in der US 5,013,289 beschriebenes Getriebe, welches einen Vorgelegegetriebebereich und zwei Planetensatze aufweist. Zwischen einer Getriebeeingangswel- le und einem hierzu nicht koaxial angeordneten Abtrieb sind drei Leistungspfade vorgesehen, in denen mittels einer Lastschaltung die Übersetzung veränderbar ist. Durch die Bereitstellung von drei mit den Planetensatzen verbindbaren Leistungspfaden können sechs Vorwartsgange mit verhaltnis- maßig wenigen Schaltelementen realisiert werden.A combination of features of the transmission types described above shows a transmission described in US Pat. No. 5,013,289, which has a countershaft transmission area and two planetary gears. Three power paths are provided between a transmission input shaft and an output which is not arranged coaxially for this purpose, in which the gear ratio can be changed by means of a load shift. By providing three power paths that can be connected to the planetary gear sets, six forward gears can be realized with a relatively small number of switching elements.
Nachteilig ist hierbei jedoch, daß die Lastschaltung die Verwendung von Lamellenkupplungen mit einem entsprechend großen Aufwand bezuglich der Konstruktion, der hy- draulischen Steuerung und der Regelung erfordert. Weiter nachteilig ist hier, daß zur Versorgung des aufwendigen Hydrauliksystems eine Hochdruckhydraulikpumpe vorgesehen werden muß, welche mit den sich einstellenden Ξchleppverlu- sten zu einer Reduzierung des Systemwirkungsgrades fuhrt.The disadvantage here, however, is that the power shift requires the use of multi-plate clutches with a correspondingly high outlay in terms of construction, hydraulic control and regulation. Another disadvantage here is that a high-pressure hydraulic pump is provided to supply the complex hydraulic system which leads to a reduction in the system efficiency with the resulting towing losses.
Es ist Aufgabe der vorliegenden Erfindung, ein automa- tisiertes Mehrgang-Fahrzeuggetriebe zur Verfügung zu stellen, welches gegenüber dem aufgezeigten Stand der Technik dahingehend verbessert ist, daß es auch bei einer höheren Anzahl an zu schaltenden Gangen konstruktiv kompakt und möglichst einfach mit geringem Bauraumbedarf ausfuhrbar ist und eine gute Fahrbarkeit aufweist.It is an object of the present invention to provide an automated multi-speed vehicle transmission which is improved over the prior art shown in that it can be designed in a structurally compact manner and with as little space as possible, even with a higher number of gears to be shifted is and has good driveability.
Diese Aufgabe wird mit einem automatisierten Mehrgang- Fahrzeuggetriebe gemäß den Merkmalen des Patentanspruches 1 gelost .This object is achieved with an automated multi-speed vehicle transmission according to the features of claim 1.
Ein Mehrgang-Fahrzeuggetriebe der eingangs genannten Art, bei dem mindestens eine Übersetzung formschlussig geschaltet wird, bietet den Vorteil, daß es gegenüber Plane- ten-Lastschaltautomatgetrieben eine deutlich einfachere und kostengünstigere Konstruktion aufweist, da zumindest teilweise auf ein aufwendiges Hydrauliksystem für die Schaltelemente verzichtet werden kann. Wegen des fehlenden oder zumindest geringeren Einsatzes von Hydraulik mit den damit verbundenen Schleppverlusten wird ein besserer Wirkungsgrad erzielt.A multi-speed vehicle transmission of the type mentioned at the outset, in which at least one gear ratio is switched positively, offers the advantage that it has a significantly simpler and more cost-effective construction than planetary powershift transmissions, since at least some of the complex hydraulic systems for the shifting elements are dispensed with can. Due to the lack of or at least less use of hydraulics with the associated drag losses, better efficiency is achieved.
Besonders hervorzuheben ist bei dem erfindungsgemaßen Getriebe die geringe Anzahl an benotigten Bauteilen. So reichen zu seiner Realisierung bereits eine einfach Vorge- legewelle und wenige Planetensatze, welche wenig Bauraum beanspruchen und hinsichtlich der Laufgerausche ruhig sind. Durch die Leistungsverzweigung ergibt sich eine weitere Verbesserung des Wirkungsgrades und eine geringe Belastung der Schaltelemente.Particularly noteworthy in the transmission according to the invention is the small number of components required. A simple countershaft and a few planetary gears, which take up little installation space and are quiet in terms of running noise, are sufficient for its implementation. The power split results in another one Improvement in efficiency and a low load on the switching elements.
In einer vorteilhaften Ausführung eines erfindungsge- mäßen Mehrgang-Fahrzeuggetriebes als Sechs-Gang-Getriebe können z.B. zwei Leistungspf de vorgesehen sein, wobei das Planetensatz-Summiergetriebe als Drei-Wellen-Getriebe mit einfachem Planetensatz ausgeführt ist. Gegenüber einem konventionellen Sechs-Gang-Vorgelegegetriebe ist ein solches Getriebe z.B. mit vier Vorgelegeradebenen statt sieben Vorgelegeradebenen und nur sechs statt sieben Synchronisierungen realisierbar.In an advantageous embodiment of a multi-speed vehicle transmission according to the invention as a six-speed transmission, e.g. Two power de can be provided, the planetary gear summing gear being designed as a three-shaft gear with a simple planetary gear. Compared to a conventional six-speed countershaft transmission, such a transmission is e.g. Realizable with four countershaft levels instead of seven countershaft levels and only six instead of seven synchronizations.
Bei Verwendung eines zusammengesetzten Planetensatzes bei dem Planetensatz-Summiergetriebe kann das erfindungsgemäße Mehrgang-Fahrzeuggetriebe in einer vorteilhaften Ausführung mit drei Leistungspfaden ausgestattet sein, wobei das Planetensatz-Summiergetriebe als Vier-Wellen-Getriebe mit zweifachem Planetensatz ausgeführt ist. Zur Realisie- rung von sechs Vorwärtsgängen reichen hier zwei Radebenen und fünf Synchronisierungen aus.When a composite planetary gear set is used in the planetary gear set summing gear, the multi-speed vehicle transmission according to the invention can be equipped in an advantageous embodiment with three performance paths, the planetary gear set summing gear being designed as a four-shaft gear unit with a double planetary gear set. Two wheel planes and five synchronizations are sufficient to implement six forward gears.
In weiteren Ausführungen können auch mehr als drei Leistungspfade vorgesehen sein, wobei das Planetensatz- Summiergetriebe dann aus mindestens vier Wellen aufgebaut ist.In further versions, more than three power paths can also be provided, the planetary gear summing gear then being constructed from at least four shafts.
Wenn die Übersetzungen in den einzelnen Leistungspfaden auch gleich sein können, so ist es in der Regel dennoch zweckmäßig, wenn die Leistungspfade voneinander unterschiedliche Übersetzungen aufweisen. Wenigstens in einem der Leistungspfade muß die Übersetzung veränderbar sein. Erfindungsgemäß sind die Übersetzungen nicht stufenlos va- riabel, sondern als Stirnradübersetzungen oder als direkte Verbindung ausgeführt, wobei sie vorzugsweise alle formschlüssig durch Synchronisierungen oder Klauenkupplungen, welche jeweils zwei Wellen oder eine Welle und ein Gehäuse verbinden, geschaltet werden.If the translations in the individual performance paths can also be the same, it is usually still expedient if the performance paths have different translations. The translation must be changeable in at least one of the performance paths. According to the invention, the translations are not continuously variable. riabel, but designed as spur gear ratios or as a direct connection, preferably all of which are positively connected by synchronizations or claw couplings, each of which connects two shafts or a shaft and a housing.
Die Anordnung der Schaltelemente, von denen immer mindestens zwei gleichzeitig geschaltet sind, wird dabei bevorzugt so gewählt, daß die Synchronisierungen oder Klauen- kupplungen zu Paaren zusammengefaßt und als Synchron- oder Klauenpakete mit einer Kraftbetätigung schaltbar sind, d.h. daß beispielsweise in einer vorteilhaften Ausführung zwei Klauenkupplungen durch eine Schaltgabel betätigbar sind, wobei jeweils nur eine oder keine der Klauenkupplungen be- rätigt wird.The arrangement of the switching elements, of which at least two are always switched at the same time, is preferably selected so that the synchronizations or claw clutches are combined into pairs and can be switched as synchronous or claw packets with a power actuation, i.e. that, for example, in an advantageous embodiment, two dog clutches can be actuated by a shift fork, only one or none of the dog clutches being actuated in each case.
Weitere Vorteile und vorteilhafte Ausgestaltungen eines automatisierten Mehrgang-Fahrzeuggetriebes nach der Erfindung sind der Beschreibung, der Zeichnung und den Pa- tentansprüchen entnehmbar.Further advantages and advantageous configurations of an automated multi-speed vehicle transmission according to the invention can be found in the description, the drawing and the patent claims.
Mehrere Ausführungsbeispiele eines automatisierten Mehrgang-Fahrzeuggetriebes nach der Erfindung sind in der Zeichnung schematisch vereinfacht dargestellt und werden in der nachfolgenden Beschreibung näher erläutert.Several exemplary embodiments of an automated multi-speed vehicle transmission according to the invention are shown schematically simplified in the drawing and are explained in more detail in the following description.
Es zeigt:It shows:
Fig.l ein Prinzipschema einer ersten Variante eines erfindungsgemäßen automatisierten Mehrgang-Fig.l is a schematic diagram of a first variant of an automated multi-speed
Fahrzeuggetriebes, dessen Summiergetriebe einen einfachen Planetensatz aufweist; Fig. 2a ein Getriebeschema eines Ausfuhrungsbeispieles der ersten Variante des erfindungsgema- ßen Mehrgang-Fahrzeuggetriebes;Vehicle transmission, the summing gear has a simple planetary gear set; 2a shows a transmission diagram of an exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention;
Fig. 2b eine zu dem Getriebeschema nach Fig. 2a gehörige Schaltlogik;FIG. 2b shows a switching logic belonging to the transmission diagram according to FIG. 2a;
Fig. 3a ein Getriebeschema eines weiteren Ausfuhrungsbeispieles der ersten Variante des er- findungsgemaßen Mehrgang-Fahrzeuggetriebes;3a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention;
Fig. 3b eine zu dem Getriebeschema nach Fig. 3a gehörige Schaltlogik;3b shows a switching logic belonging to the transmission diagram according to FIG. 3a;
Fig. 4a ein Getriebeschema eines weiteren Ausfuhrungsbeispieles der ersten Variante des er- findungsgemaßen Mehrgang-Fahrzeugge riebes;4a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention;
Fig. 4b eine zu dem Getriebeschema nach Fig. 4a ge- hörige Schaltlogik;FIG. 4b shows a switching logic belonging to the transmission diagram according to FIG. 4a;
Fig. 5 ein Prinzipschema einer zweiten Variante eines erfindungsgemaßen Mehrgang- Fahrzeuggetriebes, dessen Summiergetriebe einen zweifachen Planetensatz aufweist;5 shows a basic diagram of a second variant of a multi-speed vehicle transmission according to the invention, the summation transmission of which has a double planetary gear set;
Fig. 6a ein Getriebeschema eines Ausfuhrungsbeispiels des Mehrgang-Fahrzeuggetriebes gemäß der zweiten Variante nach Fig. 4;6a shows a transmission diagram of an exemplary embodiment of the multi-speed vehicle transmission according to the second variant according to FIG. 4;
Fig. 6b eine zu dem Getriebeschema nach Fig. 6a gehörige Schaltlogik; Fig. 7a ein Getriebeschema eines zweiten Ausfuhrungsbeispieles eines Mehrgang-Fahrzeuggetriebes gemäß der zweiten Variante nach Fig. 4; undFIG. 6b shows a switching logic belonging to the transmission diagram according to FIG. 6a; 7a shows a transmission diagram of a second exemplary embodiment of a multi-speed vehicle transmission according to the second variant according to FIG. 4; and
Fig. 7b eine zu dem Getriebeschema nach Fig. 7a gehörige Schaltlogik.7b shows a shifting logic belonging to the transmission scheme according to FIG. 7a.
In Fig. 1 ist ein Prinzipschema einer ersten Variante eines automatisierten Mehrgang-Fahrzeuggetriebes 1 dargestellt, welches vorliegend sechs Vorwartsgange und einen Rückwärtsgang aufweist.1 shows a basic diagram of a first variant of an automated multi-speed vehicle transmission 1, which in the present case has six forward gears and one reverse gear.
Hierzu weist das Fahrzeuggetriebe 1 zwischen einer Eingangswelle bzw. Antriebswelle 2 und einer mit einem Abtrieb verbundenen Ausgangswelle 3 ein Vorgelegegetriebe 4 und ein Planetensatz-Summiergetriebe 5 auf, welches vorliegend ein Differential ist und als Drei-Wellen-Getriebe mit einfachem Planetensatz ausgeführt ist. Die Leistung der Eingangswelle 2 ist auf zwei Leistungspfade Pl, P2 aufteilbar, wobei ein erster Leistungspfad Pl mit einer ersten Welle 6 und ein zweiter Leistungspfad P2 mit einer zweiten Welle 7 des Drei-Wellen-Getriebes 5 verbunden ist. Die dritte Welle des Drei-Wellen-Getriebes 5 stellt die mit dem Abtrieb verbundene Ausgangswelle 3 dar.For this purpose, the vehicle transmission 1 has, between an input shaft or drive shaft 2 and an output shaft 3 connected to an output, a countershaft transmission 4 and a planetary gear summing gear 5, which in the present case is a differential and is designed as a three-shaft gear with a simple planetary gear set. The power of the input shaft 2 can be divided into two power paths P1, P2, a first power path P1 being connected to a first shaft 6 and a second power path P2 being connected to a second shaft 7 of the three-shaft transmission 5. The third shaft of the three-shaft gear 5 represents the output shaft 3 connected to the output.
Bei den einzelnen Leistungspfaden Pl, P2 sind jeweils Übersetzungsstufen il, i2 bzw. i3 vorgesehen, welche bevorzugt in Vorgelegebauweise ausgestaltet sind. In dem ersten Leistungspfad Pl sind zwei parallel angeordnete feststehende Übersetzungen il, i2 vorgesehen, welche über zugeordnete Kupplungen Kl bzw. K2 zugeschaltet werden können. In dem zweiten Leistungspfad P2 ist ebenfalls eine feststehende Übersetzung ι3 vorgesehen, die über eine zugeordnete Kupplung K3 in den Leistungsfluß geschaltet werden kann.For the individual power paths P1, P2, translation stages il, i2 and i3 are provided, which are preferably designed in the countershaft design. In the first power path P1, two fixed translations i1, i2 arranged in parallel are provided, which can be connected via assigned clutches K1 or K2. There is also a fixed one in the second power path P2 Translation ι3 provided that can be switched into the power flow via an associated clutch K3.
Mit den drei vorgegebenen Übersetzungen il, i2 und i3, einer überbrückenden Kupplung K4 und einer am Getriebege- hause abgestutzten Bremse BR können sechs Gange für Vor- wartsfahrt, welche aus Gründen einer komfortableren Fahrbarkeit progressiv gestuft sind, geschaltet werden. Ein Rückwärtsgang kann entweder durch eine zusatzliche Stirn- radstufe mit integrierter Drehzahlumkehr oder durch eine Drehzahlumkehr im Planetensatz verwirklicht werden.With the three predefined ratios il, i2 and i3, a bridging clutch K4 and a brake BR supported on the gearbox housing, six gears can be shifted for forward travel, which are progressively graded for reasons of more comfortable driveability. A reverse gear can be achieved either by an additional spur gear stage with integrated speed reversal or by a speed reversal in the planetary gear set.
In den Fig. 2a und Fig. 2b ist ein Getriebe- und Schaltschema eines solchen automatisierten Mehrgang- Fahrzeuggetriebes gezeigt. Zur Realisierung von sechs Vor- wartsgangen und einem Rückwärtsgang sind sechs for schlus- sig zu schaltende Schaltelemente bzw. Kupplungen A, B, C, D, E und F sowie ein als Drei-Wellen-Getriebe ausgeführtes Planetensatz-Summiergetriebe 5 vorgesehen. Zur Ausfuhrung des Rückwärtsganges ist zudem ein Ruckwartsgangrad 8 zwischen der Kupplung C und der Vorgelegewelle 9 vorgesehen. Die Schaltungen erfolgen über Synchronisierungen 39 oder Klauenkupplungen .2a and 2b show a transmission and shifting diagram of such an automated multi-speed vehicle transmission. In order to implement six forward gears and one reverse gear, six shifting elements or clutches A, B, C, D, E and F that are to be switched as well as a planetary gear summing gear 5 designed as a three-shaft gear are provided. To perform the reverse gear, a reverse gear 8 is also provided between the clutch C and the countershaft 9. The gearshifts are made via synchronizers 39 or dog clutches.
Das Planetensatz-Summiergetriebe 5 ist bei der in Fig. 2a gezeigten Ausfuhrung ein einfacher Planetenradsatz, welcher zwischen einem Sonnenrad 10 und einem Hohlrad 11 walzende Planetenrader 12 aufweist, deren Planetenradtrager mit der zum Abtrieb fuhrenden Ausgangswelle 3 fest verbun- den sind.In the embodiment shown in FIG. 2 a, the planetary gear set summing gear 5 is a simple planetary gear set, which has planet gears 12 that roll between a sun gear 10 and a ring gear 11, the planet gear carriers of which are firmly connected to the output shaft 3 leading to the output.
Wie der zugehörigen Schaltlogik in Fig. 2b zu entnehmen ist, ist die Gangstufung progressiv, d.h. daß der Sprung der Übersetzung i zwischen den Gängen mit höher werdender Gangzahl immer geringer wird.As can be seen from the associated shifting logic in FIG. 2b, the gear step is progressive, ie that the Jump of the ratio i between the gears with increasing number of gears becomes less and less.
Die Fig. 3a und Fig. 3b zeigen ein im wesentlichen der Ausführung nach Fig. 2a und Fig. 2b entsprechendes Getriebeschema mit zugehöriger Schaltlogik, wobei hier eine größere Spreizung des Getriebes durch die Ausgestaltung des Planetensatz-Summiergetriebes 5 mit zwischen einem Sonnenrad 13 und einem mit der Ausgangswelle 3 fest verbundenen Hohlrad 14 radial nebeneinander angeordneten Planetenrädern 15, 16, die auf einem gemeinsamen Planetenradträger 17 gelagert sind, erreicht wird.FIGS. 3a and 3b show a transmission diagram essentially corresponding to the embodiment according to FIGS. 2a and 2b, with associated shift logic, with a greater spread of the transmission here due to the design of the planetary gear summing transmission 5 with between a sun gear 13 and a with the output shaft 3 fixedly connected ring gear 14 radially adjacent planet gears 15, 16 which are mounted on a common planet carrier 17 is achieved.
Die Fig. 4a und Fig. 4b zeigen eine weitere, im we- sentlichen der Ausführung nach Fig. 2a und Fig. 2b sowie Fig. 3a und Fig. 3b entsprechende Variante der Getriebeschaltung mit zugehöriger Schaltlogik, weshalb auf die analogen Getriebekomponenten hier nicht weiter eingegangen wird. Jedoch ist hier der Rückwärtsgang nicht durch eine Stirnradstufe mit Zwischenrad wie bei der Ausführung nach Fig. 2a und Fig. 3a verwirklicht, sondern durch eine Drehrichtungsumkehr im Planetensatz des Planetensatz- Summiergetriebes 5. Eine solche Drehrichtungsumkehr wird durch ein Festhalten und Abstützen eines Hohlrades 53 des Planetensatzes mittels des Schaltelementes A an einem Gehäuse 40 des Getriebes erreicht.FIGS. 4a and 4b show a further variant of the gear shift with the associated shift logic, which essentially corresponds to the embodiment according to FIGS. 2a and 2b as well as FIGS. 3a and 3b, which is why the analog gear components are not further discussed here is received. However, here the reverse gear is not realized by a spur gear stage with an intermediate gear as in the embodiment according to FIGS. 2a and 3a, but by a reversal of the direction of rotation in the planetary gear set of the planetary gear set 5. Such a reversal of the direction of rotation is achieved by holding and supporting a ring gear 53 Planet set reached by means of the switching element A on a housing 40 of the transmission.
Die Fig. 5 zeigt ein Prinzipschema einer zweiten Variante eines automatisierten Sechs-Gang-Fahrzeuggetriebes 1.5 shows a schematic diagram of a second variant of an automated six-speed vehicle transmission 1.
Bei dieser Variante ist die Leistung der Eingangswelle 2 in drei Leistungspfade P10, P20 und P30 auftrennbar, welche über entsprechende Eingangswellen 18, 19, 20 in ein Planetensatz-Summiergetriebe 50 munden, das hier als Doppeldifferential in Form eines Vier-Wellen-Getriebes mit zweifachem Planetensatz ausgeführt ist. Mit den drei Leistungspfaden P10, P20 und P30, mit den jeweils zugeordneten Übersetzungen ilO, i20, i30 und Kupplungen K10, K20, K30 sowie zwei an dem Getriebegehause abgestutzten Schaltelementen bzw. Bremsen Bl und B2 können sechs Vorwartsgange und ein Rückwärtsgang ausgef hrt werden. Dabei werden jeweils zwei der drei Leistungspfade P10, P20 und P30 in dem Planetensatz-Summiergetriebe 5 kombiniert.In this variant, the power of the input shaft 2 can be separated into three power paths P10, P20 and P30, which via corresponding input shafts 18, 19, 20 Planet gear summing gear 50 mouth, which is designed here as a double differential in the form of a four-shaft gear with a double planetary gear. With the three performance paths P10, P20 and P30, with the respective assigned ratios ilO, i20, i30 and clutches K10, K20, K30 as well as two shift elements or brakes Bl and B2 supported on the transmission housing, six forward gears and one reverse gear can be carried out. Two of the three power paths P10, P20 and P30 are combined in the planetary gear summing gear 5.
Neben der Realisierung von zusatzlichen Übersetzungen durch die Schaltelemente bzw. Bremsen Bl und B2 kann statt einer der Bremsen Bl, B2 auch noch eine zusatzliche Kupp- lung zwischen zweien der Leistungspfade vorgesehen sein.In addition to the realization of additional translations by the switching elements or brakes B1 and B2, instead of one of the brakes B1, B2, an additional clutch can also be provided between two of the power paths.
Ein Ausfuhrungsbeispiel einer solchen Variante eines Mehrgang-Fahrzeuggetriebes ist in der Fig. 6a und Fig. 6b gezeigt, welches zum Schalten von sechs Vorwartsgangen fünf for schlussig zu schaltende Schaltelemente A, B, C, D, E und ein Planetensatz-Summiergetriebe 50, welches ein Vier- Wellen-Getriebe mit zweifachem Planetensatz darstellt, aufweist. Das Planetensatz-Summiergetriebe 50 besteht hier aus einem gemeinsamen, mit der zum Abtrieb fuhrenden Ausgangs- welle 3 fest verbundenen Hohlrad 21, zwei verschieden großen Sonnenrädern 22, 23 und zwischen diesen und dem Hohlrad 21 walzenden Planetenradern 24, 25 unterschiedlicher Lange, welche einen gemeinsamen Planetenradtrager 26 aufweisen. Damit entspricht das Planetensatz-Summiergetriebe 50 im wesentlichen einem bekannten Ravigneaux-Satz . Die Verbindung zur Vorgelegewelle 27 wird über zwei Radebenen 28, 29 hergestellt . In Fig. 7a und Fig. 7b ist ein weiteres Ausführungsbeispiel der zweiten Variante eines erfindungsgemäßen automatisierten Mehrgang-Fahrzeuggetriebes gezeigt, bei dem das Planetensatz-Summiergetriebe 50 ein typischer Vier-Wellen- Satz mit einem gemeinsamen Sonnenrad 30, zwei HohlrädernAn exemplary embodiment of such a variant of a multi-speed vehicle transmission is shown in FIGS. 6a and 6b, which for shifting six forward gears five shifting elements A, B, C, D, E to be switched and a planetary gear summing gear 50 which represents a four-shaft transmission with two planetary gear sets. The planetary gear summing gear 50 here consists of a common ring gear 21, which is fixedly connected to the output shaft 3 leading to the output, two sun gears 22, 23 of different sizes, and planet gears 24, 25 of different lengths which roll between them and the ring gear 21 and which have a common length Have planet carrier 26. The planetary gear summing gear 50 thus essentially corresponds to a known Ravigneaux gear. The connection to the countershaft 27 is established via two wheel planes 28, 29. 7a and 7b show a further exemplary embodiment of the second variant of an automated multi-speed vehicle transmission according to the invention, in which the planetary gear summing gear 50 is a typical four-shaft set with a common sun gear 30, two ring gears
31, 32 mit gleichem Durchmesser und zwei Planetenradträgern 33, 34 mit darauf gelagerten Planetenrädern ist. Die Ausgangswelle 3 ist mit einem der Planetenträger 34 verbunden.31, 32 with the same diameter and two planet gear carriers 33, 34 with planet gears mounted thereon. The output shaft 3 is connected to one of the planet carriers 34.
Im Unterschied zu der Ausführung nach Fig. 6a und Fig. 6b ist hier das Planetensatz-Summiergetriebe 50 im Leistungsstrang zwischen den allesamt formschlüssigen Schaltelementen A, E, C einerseits und B, F andererseits angeordnet, wobei die Planetensatzanordnung einfacher gebaut wer- den kann, da die Querkräfte der Stirnradstufen gehäusenah abgestützt sind.In contrast to the embodiment according to FIGS. 6a and 6b, here the planetary gear summing gear 50 is arranged in the power train between the all form-fitting shifting elements A, E, C on the one hand and B, F on the other hand, the planetary gear arrangement being simpler to build, because the lateral forces of the spur gear stages are supported close to the housing.
Bei der Ausführung des Sechs-Gang-Fahrzeuggetriebes nach Fig. 7a und Fig. 7b ist die Vorgelegewelle 35 über drei Radebenen 36, 37, 38 mit der Eingangswelle 2 und den Schaltelementen verbindbar.In the embodiment of the six-speed vehicle transmission according to FIGS. 7a and 7b, the countershaft 35 can be connected to the input shaft 2 and the shifting elements via three wheel planes 36, 37, 38.
Die Gangstufung ist, wie der jeweiligen Schaltlogik zu entnehmen ist, sowohl bei der Ausführung nach Fig. 6a und Fig. 6b als auch bei der Ausführung nach Fig. 7a und Fig. 7b progressiv ausgelegt.As can be seen from the respective switching logic, the gear ratio is designed progressively both in the embodiment according to FIGS. 6a and 6b and in the embodiment according to FIGS. 7a and 7b.
Das erfindungsgemäße Mehrgang-Fahrzeuggetriebe ist selbstverständlich nicht auf die gezeigten Ausführungen als Sechs-Gang-Fahrzeuggetriebe limitiert, sondern ist auch für Getriebe mit einer anderen, insbesondere höheren Gangzahl geeignet . Auch ist die Anordnung der einzelnen Elemente in den gezeigten Ausführungsbeispielen nicht zwingend, da beispielsweise das Planetensatz-Summiergetriebe, wie bereits die Ausführung nach Fig. 6 zeigt, an unterschiedlichen Stellen zwischen der Eingangswelle und der Ausgangswelle des Fahrzeuggetriebes angeordnet sein kann.The multi-speed vehicle transmission according to the invention is of course not limited to the designs shown as a six-speed vehicle transmission, but is also suitable for transmissions with a different, in particular higher number of gears. The arrangement of the individual elements in the exemplary embodiments shown is also not mandatory, since, for example, the planetary gear summation gear, as already shown in the embodiment according to FIG. 6, can be arranged at different points between the input shaft and the output shaft of the vehicle transmission.
Wenngleich in den gezeigten bevorzugten Ausfuhrungen eine jede Übersetzung formschlussig geschaltet wird, kann es gegebenenfalls auch vorgesehen sein, daß zusatzlich zu den formschlussigen Schaltelementen auch kraft- oder reib- schlussige Schaltelemente eingesetzt werden. Although in the preferred embodiments shown each gear ratio is switched positively, it can also be provided that non-positive or frictional shifting elements are used in addition to the positively locking shifting elements.
Bezugszeichenreference numeral
1 Mehrgang-Fahrzeuggetriebe1 multi-speed vehicle transmission
2 Eingangswelle des Fahrzeuggetriebes 3 Ausgangswelle des Fahrzeuggetriebes2 Input shaft of the vehicle transmission 3 Output shaft of the vehicle transmission
4 Vorgelegegetriebe4 countershaft transmission
5 Planetensatz-Summiergetriebe, Differential 6,7,8 Welle5 planetary gear summing gear, differential 6,7,8 shaft
9 Vorgelegewelle 10 Sonnenrad9 countershaft 10 sun gear
11 Hohlrad11 ring gear
12 Planetenrad12 planet gear
13 Sonnenrad13 sun gear
14 Hohlrad 15,16 Planetenrad14 ring gear 15, 16 planet gear
17 Planetenradträger 18, 19,21 Welle17 planet carrier 18, 19.21 shaft
20 Welle20 wave
21 Hohlrad 22,23 Sonnenrad21 ring gear 22.23 sun gear
24 Planetenrad24 planet gear
25 Planetenrad25 planet gear
26 Planetenradträger26 planet carrier
27 Vorgelegewelle 28,29 Radebene27 countershaft 28.29 wheel plane
30 Sonnenrad30 sun gear
31,32 Hohlrad31.32 ring gear
33,34 Planetenradträger33.34 planet carrier
35 Vorgelegewelle 36,37,38 Radebene35 countershaft 36,37,38 wheel plane
39 Synchronisierung39 synchronization
40 Gehäuse40 housing
50 Planetensatz-Summiergetriebe A Schaltelement, Kupplung50 planetary gear summing gear A switching element, clutch
3 Schaltelement, Kupplung3 switching element, clutch
Bl Schaltelement, Bremse B2 Schaltelement, BremseBl switching element, brake B2 switching element, brake
BR Schaltelement, BremseBR switching element, brake
C Schaltelement, KupplungC switching element, clutch
D Schaltelement, KupplungD switching element, clutch
E Schaltelement, Kupplung F Schaltelement, Kupplung il Übersetzung i2 Übersetzung i3 Übersetzung ilO Übersetzung i20 Übersetzung i30 ÜbersetzungE switching element, clutch F switching element, clutch il translation i2 translation i3 translation ilO translation i20 translation i30 translation
Kl Schaltelement, KupplungKl switching element, clutch
K2 Schaltelement, KupplungK2 switching element, clutch
K3 Schaltelement, Kupplung K4 Schaltelement, KupplungK3 switching element, clutch K4 switching element, clutch
Pl LeistungspfadPl power path
P2 LeistungspfadP2 power path
P3 LeistungspfadP3 power path
P10 Leistungspfad P20 LeistungspfadP10 power path P20 power path
P30 Leistungspfad P30 power path

Claims

P a t e n t a n s p r u e h e Patent claims
1. Automatisiertes Mehrgang-Fahrzeuggetriebe, bei dem zwischen einer Eingangswelle (2) und einer Ausgangswelle (3) zur Schaltung der Gänge mehrere Leistungspfade (Pl, P2; P10, P20, P30) vorgesehen sind, die in einem Planetensatz-Summiergetriebe (5; 50) summiert werden, wobei in wenigstens einem der Leistungspfade (Pl, P2; P10, P20, P30) die Übersetzung (il, i2, i3; ilO, i20, i30) gestuft veränderbar ist, und wobei mindestens eine Übersetzung (il, i2, i3; ilO, i20, i30) formschlüssig geschaltet wird.1. Automated multi-speed vehicle transmission, in which a plurality of power paths (Pl, P2; P10, P20, P30) are provided between an input shaft (2) and an output shaft (3) for shifting the gears. 50) are summed, the translation (il, i2, i3; ilO, i20, i30) being changeable in steps in at least one of the power paths (P1, P2; P10, P20, P30), and at least one translation (il, i2 , i3; ilO, i20, i30) is switched positively.
2. Automatisiertes Mehrgang-Fahrzeuggetriebe nach Anspruch2. Automated multi-speed vehicle transmission according to claim
1, dadurch g e k e n n z e i c h n e t , daß zwei Leistungspfade (Pl, P2) vorgesehen sind, wobei das Planetensatz-Summiergetriebe (5) als Drei-Wellen-Getriebe ausgeführt ist.1, characterized by the fact that two power paths (Pl, P2) are provided, the planetary gear summing gear (5) being designed as a three-shaft gear.
3. Automatisiertes Mehrgang-Fahrzeuggetriebe nach Anspruch3. Automated multi-speed vehicle transmission according to claim
2, dadurch g e k e n n z e i c h n e t , daß das Drei-Wellen-Getriebe (5) einen einfachen Planetensatz (5) aufweist.2, characterized by the fact that the three-shaft gear (5) has a simple planetary gear set (5).
4. Automatisiertes Mehrgang-Fahrzeuggetriebe nach Anspruch 1, dadurch g e k e n n z e i c h n e t , daß wenigstens drei Leistungspfade (P10, P20, P30) vorgesehen sind, wobei das Planetensatz-Summiergetriebe (50) als mindestens vierwelliges Getriebe ausgeführt ist. 4. Automated multi-speed vehicle transmission according to claim 1, characterized in that at least three power paths (P10, P20, P30) are provided, the planetary gear summing gear (50) being designed as an at least four-shaft gear.
. Automatisiertes Mehrgang-Fahrzeuggetriebe nach Anspruch 4, dadurch g e k e n n z e i c h n e t , daß das Planetensatz-Summiergetriebe als Vier-Wellen-Getriebe (50) ausgeführt ist, das einen zweifachen Planetensatz aufweist., Automated multi-speed vehicle transmission according to claim 4, characterized in that the planetary gear summing gear is designed as a four-shaft gear (50) which has a double planetary gear set.
6. Automatisiertes Mehrgang-Fahrzeuggetriebe nach einem der Ansprüche 1 bis 5, dadurch g e k e n n z e i c h n e t , daß die formschlussig geschalteten Ubersetzun- gen (il, ι2, ι3; ilO, i20, i30) als Stirnradubersetzun- gen oder als direkte Verbindung ausgeführt sind.6. Automated multi-speed vehicle transmission according to one of claims 1 to 5, characterized in that the form-fit gear ratios (il, ι2, ι3; ilO, i20, i30) are designed as spur gear ratios or as a direct connection.
7. Automatisiertes Mehrgang-Fahrzeuggetriebe nach einem der Ansprüche 1 bis 6, dadurch g e k e n n - z e i c h n e t , daß die Übersetzungen (il, i2, ι3; ilO, i20, i30) durch Synchronisierungen (39) oder Klauenkupplungen formschlussig geschaltet werden.7. Automated multi-speed vehicle transmission according to one of claims 1 to 6, characterized g e k e n n - z e i c h n e t that the translations (il, i2, ι3; ilO, i20, i30) are switched positively by synchronizations (39) or dog clutches.
8. Automatisiertes Mehrgang-Fahrzeuggetriebe nach Anspruch 7, dadurch g e k e n n z e i c h n e t , daß die8. Automated multi-speed vehicle transmission according to claim 7, characterized g e k e n n z e i c h n e t that the
Synchronisierungen (39) oder Klauenkupplungen jeweils zwei Wellen oder eine Welle mit einem Gehäuse (40) verbinden .Connect synchronizers (39) or dog clutches two shafts or one shaft to a housing (40).
9. Automatisiertes Mehrgang-Fahrzeuggetriebe nach einem der Ansprüche 1 bis 8, dadurch g e k e n n z e i c h n e t , daß die Anordnungen so gewählt sind, daß Synchronisierungen (39) oder Klauenkupplungen zu Paaren zusammengelegt und als Synchron- oder Klauen- pakete mit einer Kraftbetatigung schaltbar sind.9. Automated multi-speed vehicle transmission according to one of claims 1 to 8, characterized in that the arrangements are selected such that synchronizations (39) or claw clutches are combined into pairs and can be switched as synchronous or claw packets with power actuation.
10. Automatisiertes Mehrgang-Fahrzeuggetriebe nach einem der Ansprüche 1 bis 9, dadurch g e k e n n - z e i c h n e t , daß jeweils mindestens zwei Schaltelemente (A, B, Bl, B2, C, D, E, F, Kl, K2, K3, K4 ) gleichzeitig geschaltet sind.10. Automated multi-speed vehicle transmission according to one of claims 1 to 9, characterized in - is characterized in that at least two switching elements (A, B, Bl, B2, C, D, E, F, Kl, K2, K3, K4) are switched simultaneously.
11. Automatisiertes Mehrgang-Fahrzeuggetriebe nach einem der Ansprüche 1 bis 10, dadurch g e k e n n z e i c h n e t , daß die Gangstufung progressiv ist, 11. Automated multi-speed vehicle transmission according to one of claims 1 to 10, characterized in that the gear ratio is progressive,
PCT/EP2002/009623 2001-09-14 2002-08-29 Automatic multi-speed vehicle gearbox WO2003025431A1 (en)

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DE2001145519 DE10145519A1 (en) 2001-09-14 2001-09-14 Automated multi-speed vehicle transmission
DE10145519.4 2001-09-14

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* Cited by examiner, † Cited by third party
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WO2006032312A1 (en) 2004-09-23 2006-03-30 Daimlerchrysler Ag Automated transmission for a motor vehicle and method for operating the same
GB2471859A (en) * 2009-07-15 2011-01-19 Alvan Burgess Transmission comprising an infinitely variable drive and a differential
US8287416B2 (en) 2010-03-31 2012-10-16 GM Global Technology Operations LLC Eight-speed planetary layshaft transmission
US8360922B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with up to ten forward speed ratios
US8360923B2 (en) 2010-03-19 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary gear sets and layshafts
US8360924B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with two planetary gear sets and up to ten forward speed ratios
US8360919B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission
US8360925B2 (en) 2010-03-01 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with compound and simple planetary gear sets and with layshafts
US8360918B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary and layshaft gears
US8398524B2 (en) 2010-03-19 2013-03-19 GM Global Technology Operations LLC Multi-speed transmission with eight torque-transmitting mechanisms
US8439787B2 (en) 2010-03-19 2013-05-14 GM Global Technology Operations LLC Transmission with mixed planetary layshaft structure
US8540600B2 (en) 2010-03-03 2013-09-24 GM Global Technology Operations LLC Multi-speed planetary transmission with three brakes and four clutches
US11209075B2 (en) * 2019-07-22 2021-12-28 Deere & Company Transmission

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DE10250480B4 (en) 2002-10-30 2018-02-01 Zf Friedrichshafen Ag Automated multi-speed manual transmission
DE10315313A1 (en) * 2003-04-04 2005-01-20 Zf Friedrichshafen Ag Transmission, in particular automated power-split multi-speed transmission
DE10322234A1 (en) * 2003-05-17 2004-12-23 Zf Friedrichshafen Ag Two-gang gear mechanism especially for ships' drives includes a second clutch to connect two input members together or one input member to output member when first clutch is open
DE102011105065A1 (en) * 2011-06-21 2012-12-27 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Double-shaft shift gearbox i.e. six-speed gearbox, for use in motor car, has gearbox drive shaft with input region comprising planetary gear stage with brake device, where gearbox is connected with motor shaft by single clutch
DE102019007129B4 (en) * 2019-10-14 2021-09-23 Daimler Ag Group transmission device, in particular split transmission

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US4682511A (en) * 1985-10-18 1987-07-28 Wittke Ernest C Gear assisted continuously variable transmission
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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006032312A1 (en) 2004-09-23 2006-03-30 Daimlerchrysler Ag Automated transmission for a motor vehicle and method for operating the same
GB2471859A (en) * 2009-07-15 2011-01-19 Alvan Burgess Transmission comprising an infinitely variable drive and a differential
US8360922B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with up to ten forward speed ratios
US8360924B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with two planetary gear sets and up to ten forward speed ratios
US8360925B2 (en) 2010-03-01 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with compound and simple planetary gear sets and with layshafts
US8540600B2 (en) 2010-03-03 2013-09-24 GM Global Technology Operations LLC Multi-speed planetary transmission with three brakes and four clutches
US8398524B2 (en) 2010-03-19 2013-03-19 GM Global Technology Operations LLC Multi-speed transmission with eight torque-transmitting mechanisms
US8360923B2 (en) 2010-03-19 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary gear sets and layshafts
US8439787B2 (en) 2010-03-19 2013-05-14 GM Global Technology Operations LLC Transmission with mixed planetary layshaft structure
US8360919B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission
US8360918B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary and layshaft gears
US8287416B2 (en) 2010-03-31 2012-10-16 GM Global Technology Operations LLC Eight-speed planetary layshaft transmission
US11209075B2 (en) * 2019-07-22 2021-12-28 Deere & Company Transmission

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