DE19821164A1 - Double clutch gearing for automobile use - Google Patents

Double clutch gearing for automobile use

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Publication number
DE19821164A1
DE19821164A1 DE19821164A DE19821164A DE19821164A1 DE 19821164 A1 DE19821164 A1 DE 19821164A1 DE 19821164 A DE19821164 A DE 19821164A DE 19821164 A DE19821164 A DE 19821164A DE 19821164 A1 DE19821164 A1 DE 19821164A1
Authority
DE
Germany
Prior art keywords
gear
transmission according
double clutch
clutch transmission
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
DE19821164A
Other languages
German (de)
Other versions
DE19821164B4 (en
Inventor
Wolfgang Schreiber
Volker Becker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
Original Assignee
Volkswagen 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 Volkswagen AG filed Critical Volkswagen AG
Priority to DE19821164A priority Critical patent/DE19821164B4/en
Publication of DE19821164A1 publication Critical patent/DE19821164A1/en
Application granted granted Critical
Publication of DE19821164B4 publication Critical patent/DE19821164B4/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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

Abstract

The double clutch hearing system comprises two concentric connected driveshafts (10) each with its own clutch (16,18), and a first and second minor shaft (48,52) with teeth (30,32,34,40,42,44,46). The minor shafts have cogs for forward and reverse drive (24,26,28,36,38). Five forward gears are incorporated, and fourth (40) and sixth (44) gears are used for reverse.

Description

Die Erfindung betrifft ein Doppelkupplungsgetriebe, insbesondere eines Kraftfahrzeuges, mit zwei konzentrisch zueinander angeordneten, mit einer Antriebswelle verbundenen, wahlweise mit jeweils einer Kupplung verbindbaren Eingangswellen und einer ersten und einer zweiten Nebenwelle, welchen jeweilige Zahnradsätze mit Zahnrädern für Vorwärtsgänge und wenigstens einem Rückwärtsgang zugeordnet sind, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a dual clutch transmission, in particular of a motor vehicle two concentrically arranged, connected to a drive shaft, optionally with a coupling connectable input shafts and a first and a second auxiliary shaft, which respective gear sets with gears for Forward gears and at least one reverse gear are assigned, according to the Preamble of claim 1.

Ein derartiges Getriebe ist aus der DE 36 10 269 A1 bekannt. Hierbei ergibt sich jedoch das Problem, daß aufgrund des großen Bauraumbedarfs eines Doppelkupplungsgetriebes dieses in einem kleinen Kraftfahrzeug nur schwer einbaubar ist.Such a transmission is known from DE 36 10 269 A1. However, this is the result Problem that due to the large space requirement of a double clutch transmission it is difficult to install in a small motor vehicle.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Doppelkupplungsgetriebe der obengenannten Art derart zu verbessern, daß sich eine kompakte Bauweise, insbesondere für einen Front-Quer-Einbau in einem Kraftfahrzeug, ergibt, wobei gleichzeitig ein hohes Drehmoment übertragbar ist.The present invention has for its object a dual clutch transmission to improve the above-mentioned type in such a way that a compact design, in particular for a front-transverse installation in a motor vehicle, results in a high Torque is transferable.

Diese Aufgabe wird erfindungsgemäß durch ein Doppelkupplungsgetriebe der o.g. Art mit den in Anspruch 1 gekennzeichneten Merkmalen gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den abhängigen Ansprüchen angegeben.This object is achieved by a dual clutch transmission of the above. Kind with solved the features characterized in claim 1. Advantageous embodiments of the Invention are specified in the dependent claims.

Dazu ist es erfindungsgemäß vorgesehen, daß für wenigstens zwei Gänge, welche jeweils einer anderen Nebenwelle zugeordnet sind, eingangswellenseitig ein einziges Zahnrad vorgesehen ist.For this purpose, it is provided according to the invention that for at least two courses, each are assigned to another countershaft, a single gearwheel on the input shaft side is provided.

Dies hat den Vorteil, daß ein Doppelkupplungsgetriebe mit hohem Wirkungsgrad, geringer Baugröße, geringem Gewicht, niedrigen Herstellungskosten, hoher Drehmomentenkapazitäten und großer Gangspreizung zur Verfügung steht. This has the advantage that a dual clutch transmission with high efficiency, less Size, light weight, low manufacturing costs, high Torque capacities and large gear spread is available.  

In einer bevorzugten Ausführungsform sind fünf Vorwärtsgänge vorgesehen, wobei für den vierten Gang und den sechsten Gang sowie für den Rückwärtsgang und den zweiten Gang eingangswellenseitig jeweils ein einziges Zahnrad vorgesehen ist, wobei insbesondere die Zahnräder der Gänge auf den Getriebeeingangswellen in Richtung Antriebswelle aufeinanderfolgend für den fünften Gang, den ersten Gang, den dritten Gang, den vierten/sechsten Gang und den Rückwärts-/zweiten Gang angeordnet sind.In a preferred embodiment, five forward gears are provided, with the fourth gear and sixth gear as well as for reverse gear and second gear a single gear is provided on the input shaft side, in particular the Gears of the gears on the transmission input shafts towards the drive shaft in succession for fifth gear, first gear, third gear, fourth / sixth gear and reverse / second gear are arranged.

Eine lastunterbrechungsfreie Schaltbarkeit in aufeinanderfolgende Gänge erzielt man dadurch, daß die Radsätze für den ersten, dritten und fünften Gang einer als Vollwelle ausgebildeten Eingangswelle und die Radsätze für den zweiten, vierten, sechsten und Rückwärtsgang einer als Hohlwelle ausgebildeten Eingangswelle zugeordnet sind.A load interruption-free switchability in successive gears is achieved characterized in that the wheelsets for the first, third and fifth gear one as a solid shaft trained input shaft and the wheel sets for the second, fourth, sixth and Reverse gear are assigned to an input shaft designed as a hollow shaft.

Zweckmäßigerweise sind der ersten Nebenwelle der fünfte, der sechste und der Rückwärtsgang in dieser Reihenfolge in Richtung Antriebswelle und der zweiten Nebenwelle der erste, dritte, vierte und zweite Gang in dieser Reihenfolge in Richtung Antriebswelle zugeordnet.The first auxiliary wave is expediently the fifth, the sixth and the Reverse in this order in the direction of the drive shaft and the second auxiliary shaft the first, third, fourth and second gear in this order towards the drive shaft assigned.

Eine kompakte Anordnung erzielt man dadurch, daß für die Gangpaare erster/dritter Gang, vierter/zweiter Gang sowie sechster Gang/ Rückwärtsgang jeweils eine gemeinsame Schiebemuffe angeordnet ist, welche die genannten Gänge jeweils wahlweise schaltet, d. h. wahlweise entsprechende Zahnradsätze mit der entsprechenden Nebenwelle verbindet.A compact arrangement is achieved in that for the gear pairs first / third gear, fourth / second gear and sixth gear / reverse gear each have a common one Sliding sleeve is arranged, which switches each of the gears mentioned, d. H. optionally connects corresponding gear sets with the corresponding countershaft.

In einer besonders bevorzugten Ausführungsform ist für den Rückwärtsgang eine dritte Nebenwelle und insbesondere für den fünften Gang eine separate Schiebemuffe vorgesehen.In a particularly preferred embodiment, a third is for the reverse gear Countershaft and especially for fifth gear a separate sliding sleeve intended.

Eine geringe Längsausdehnung des Doppelkupplungsgetriebes erzielt man insbesondere dadurch, daß zwei naß laufende Lamellenkupplungen radial zueinander angeordnet sind. Wahlweise kann die innen liegende oder außenliegende Kupplung als Anfahrkupplung verwendet werden.A small longitudinal expansion of the double clutch transmission is achieved in particular in that two wet-running multi-plate clutches are arranged radially to one another. The internal or external clutch can be used as a starting clutch be used.

Zur Druckölversorgung ist die als innenliegende Vollwelle ausgebildete Eingangswelle mit einer axialen Bohrung ausgebildet. Zweckmäßigerweise ist dabei ein Ringspalt vorgesehen, über welchen das Kühlöl einem Kupplungsgehäuse zuführbar ist. Dies erzielt eine Drucköleinspeisung mit geringem radialen Bauraumbedarf.The input shaft, which is designed as an internal solid shaft, is also used to supply pressure oil an axial bore. An annular gap is expediently provided,  via which the cooling oil can be fed to a clutch housing. This achieves one Pressure oil feed with a small radial space requirement.

Einen guten Kraftschluß für hohe Drehmomentkapazitäten erzielt man dadurch, daß die Kupplungen jeweils mit einer Eingangswelle über jeweilige Steckverzahnungen verbunden sind.A good adhesion for high torque capacities can be achieved in that the Couplings each connected to an input shaft via respective splines are.

In einer bevorzugten Ausführungsform ist in jeweiligen Kupplungskolben der Kupplungen eine Fliehkraftkompensation vorgesehen.In a preferred embodiment, the clutches are in the respective clutch pistons centrifugal force compensation is provided.

Zweckmäßigerweise ist an einem Kupplungsgehäuse eine Verzahnung zum Antrieb einer Ölpumpe vorgesehen.A toothing for driving a is expediently on a clutch housing Oil pump provided.

Zur akustischen Entkopplung ist in vorteilhafter Weise der Antriebswelle ein Zweimassenschwingungsdämpfer vorgeschaltet.The drive shaft is advantageously used for acoustic decoupling Dual mass vibration damper upstream.

Weitere Merkmale, Vorteile und vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den abhängigen Ansprüchen, sowie aus der nachstehenden Beschreibung der Erfindung anhand der beigefügten Zeichnungen. Diese zeigen inFurther features, advantages and advantageous configurations of the invention result from the dependent claims, as well as from the following description of the invention based on the attached drawings. These show in

Fig. 1 ein Ersatzschaltbild einer bevorzugten Ausführungsform eines erfindungsgemäßen Doppelkupplungsgetriebes und Fig. 1 is an equivalent circuit diagram of a preferred embodiment of a dual clutch transmission according to the invention and

Fig. 2 eine Schnittansicht der bevorzugten Ausführungsform eines erfindungsgemäßen Doppelkupplungsgetriebes von Fig. 1. FIG. 2 shows a sectional view of the preferred embodiment of a dual clutch transmission according to the invention from FIG. 1.

Die in Fig. 1 und 2 dargestellte bevorzugte Ausführungsform eines erfindungsgemäßen Doppelkupplungsgetriebes umfaßt eine Antriebswelle 10, welche über ein Schwingungsdämpfungssystem 12 mit einem Antriebsaggregat 14 verbunden ist. Abtriebsseitig ist die Antriebswelle 10 mit zwei radial zueinander angeordneten Kupplungen 16 und 18 verbunden. Hierbei schafft die Kupplung 16 eine wahlweise Verbindung zwischen der Antriebswelle 10 und einer ersten als Vollwelle ausgebildeten, radial innenliegend angeordneten Eingangswelle 20. Die Kupplung 18 schafft eine wahlweise Verbindung zwischen der Antriebswelle 10 und einer zweiten als Hohlwelle ausgebildeten, radial außenliegend angeordneten Eingangswelle 22.The preferred embodiment of a dual clutch transmission according to the invention shown in FIGS. 1 and 2 comprises a drive shaft 10 which is connected to a drive unit 14 via a vibration damping system 12 . On the output side, the drive shaft 10 is connected to two radially arranged clutches 16 and 18 . Here, the coupling 16 creates an optional connection between the drive shaft 10 and a first input shaft 20, which is designed as a solid shaft and is arranged radially on the inside. The clutch 18 creates an optional connection between the drive shaft 10 and a second input shaft 22, which is designed as a hollow shaft and is arranged radially on the outside.

Auf der ersten Eingangswelle 20 sind Zahnräder bzw. Radsätze 24, 26 und 28 für jeweils einen fünften Gang 30, einen ersten Gang 32, einen dritten Gang 34 und einen Rückwärtsgang 58 angeordnet. Auf der zweiten Eingangswelle sind Zahnräder bzw. Radsätze 36 und 38 für einen vierten Gang 40, einen zweiten Gang 42, einen sechsten Gang 44 angeordnet, wobei das Zahnrad 36 sowohl dem vierten Gang 40 als auch dem sechsten Gang 44 und das Zahnrad 26 sowohl dem ersten Gang 32 als auch dem Rückwärtsgang 58 zugeordnet ist.Gears or wheel sets 24 , 26 and 28 for a fifth gear 30 , a first gear 32 , a third gear 34 and a reverse gear 58 are arranged on the first input shaft 20 . Gear wheels 36 and 38 for a fourth gear 40 , a second gear 42 , a sixth gear 44 are arranged on the second input shaft, the gear 36 both the fourth gear 40 and the sixth gear 44 and the gear 26 both that first gear 32 and reverse gear 58 is assigned.

Die Radsätze für den fünften Gang 30, den sechsten Gang 44 und den Rückwärtsgang 46a sind einer ersten Nebenwelle 48 zugeordnet. Diese ist über ein Zahnrad 50 mit einer nicht dargestellten Abtriebswelle verbunden. Die Radsätze für den ersten Gang 32, den dritten Gang 34, den vierten Gang 40 und den zweiten Gang 42 sind einer zweiten Nebenwelle 52 zugeordnet. Diese ist über ein Zahnrad 54 mit einer Außenverzahnung 55 eines Gehäuses 59 eines Differentialgetriebes 57 verbunden. Für den Rückwärtsgang 46 ist eine dritte Nebenwelle 56 vorgesehen, welcher über ein Zahnrad 58 mit der dargestellten Antriebswelle verbunden ist.The wheel sets for fifth gear 30 , sixth gear 44 and reverse gear 46 a are assigned to a first countershaft 48 . This is connected via a gear 50 to an output shaft, not shown. The wheel sets for the first gear 32 , the third gear 34 , the fourth gear 40 and the second gear 42 are assigned to a second auxiliary shaft 52 . This is connected via a gear wheel 54 to an external toothing 55 of a housing 59 of a differential gear 57 . A third auxiliary shaft 56 is provided for the reverse gear 46 and is connected to the drive shaft shown via a gear 58 .

Eine erste Schiebemuffe 60 ist dem ersten Gang 32 und dem dritten Gang 34 zugeordnet und schaltet wahlweise diese Gänge. Eine zweite Schiebemuffe 62 ist dem vierten Gang 40 und dem zweiten Gang 42 zugeordnet und schaltet wahlweise diese Gänge. Eine dritte Schiebemuffe 64 ist dem sechsten Gang 44 und dem Rückwärtsgang 46 zugeordnet und schaltet wahlweise diese Gänge. Eine vierte Schiebemuffe 66 ist dem fünften Gang 30 zugeordnet und schaltet diesen Gang.A first sliding sleeve 60 is assigned to the first gear 32 and the third gear 34 and optionally switches these gears. A second sliding sleeve 62 is assigned to fourth gear 40 and second gear 42 and optionally switches these gears. A third sliding sleeve 64 is assigned to the sixth gear 44 and the reverse gear 46 and optionally switches these gears. A fourth sliding sleeve 66 is assigned to fifth gear 30 and switches this gear.

Durch die Anordnung der Schiebemuffen 60, 62, 64 und 66 für je ein Gangpaar und durch das Zuordnen der Zahnräder 36 und 26 für jeweils zwei Gänge auf verschiedenen Nebenwellen 48, 52 ergibt sich eine kompakte und bauraumsparende Anordnung, insbesondere bezüglich einer Längserstreckung des Doppelkupplungsgetriebes. Zusammen mit der speziellen Anordnung der Gänge auf den Eingangswellen 20, 22 in der Reihenfolge fünfter Gang 30, erster Gang 32, Rückwärtsgang 58, dritter Gang 34, vierter/sechster Gang 40, 44 und zweiter Gang 42 ergibt sich eine derart verkürzte Baulänge in Längsrichtung, d. h. in axialer Richtung bzgl. der Eingangswellen 20, 22, daß beispielsweise ein Front-Quer- Einbau in ein Kraftfahrzeug möglich ist. Die sich insbesondere aus Fig. 2 ergebende radiale Anordnung der Kupplungen 16 und 18 ergibt zusätzlich einen kleineren Bauraumbedarf des erfindungsgemäßen Doppelkupplungsgetriebes in radialer Richtung.The arrangement of the sliding sleeves 60 , 62 , 64 and 66 for each pair of gears and the assignment of the gears 36 and 26 for two gears on different auxiliary shafts 48 , 52 results in a compact and space-saving arrangement, in particular with regard to a longitudinal extension of the double clutch transmission. Together with the special arrangement of the gears on the input shafts 20 , 22 in the order of fifth gear 30 , first gear 32 , reverse gear 58 , third gear 34 , fourth / sixth gear 40 , 44 and second gear 42, this results in a shortened length in the longitudinal direction , ie in the axial direction with respect to the input shafts 20 , 22 that, for example, a front-transverse installation in a motor vehicle is possible. The radial arrangement of the clutches 16 and 18, which results in particular from FIG. 2, additionally results in a smaller installation space requirement of the dual clutch transmission according to the invention in the radial direction.

Bei dem in Fig. 1 und 2 beispielhaft dargestellten 6-Gang Zahnradwechselgetriebe ist die Anordnung der Radsätze 30, 32, 34, 40, 42, 44 und 46a für die Gänge derart ausgebildet, daß zugkraftunterbrechungsfreie Schaltungen durch eine schlupfende Betätigung der Kupplungen 16, 18 von jedem der Gänge 1/3/5 zu den Gängen 2/4/6 und umgekehrt möglich sind. Insbesondere die Anordnung der Radsätze 32, 42 für ersten und zweiten Gang und des Radsatzes 58/46 für den Rückwärtsgang sind derart ausgebildet, daß sich geringstmögliche Biegemomente an den jeweils beteiligten Wellen, insbesondere an den Eingangswellen 20, 22, ergeben.In the 6-speed gear change transmission shown by way of example in FIGS. 1 and 2, the arrangement of the wheel sets 30 , 32 , 34 , 40 , 42 , 44 and 46 a for the gears is designed in such a way that gear shift-free interruptions by a slipping actuation of the clutches 16 , 18 of each of the gears 1/3/5 are the corridors 2/4/6, and vice versa. In particular, the arrangement of the wheel sets 32, 42 for first and second gear and the gear set 58/46 for the reverse gear are formed so that the lowest possible bending moments on the respective participating waves, in particular to the input shafts 20, 22, result.

Die insbesondere als naß laufende Lamellenkupplungen ausgebildeten Kupplungen 16 und 18 gewährleisten einen geringstmöglichen Bauraumbedarf auch in axialer Richtung. Vorzugsweise dient dabei die radial innenliegende Kupplung 16 als Anfahrkupplung.The clutches 16 and 18 , which are designed in particular as wet-running multi-plate clutches, ensure the smallest possible installation space requirement, even in the axial direction. The radially inner clutch 16 preferably serves as a starting clutch.

Wie sich aus Fig. 2 ergibt, ist eine Druckölversorgung durch eine axiale Bohrung 68 der ersten Eingangswelle 20 gewährleistet. Diese Drucköleinspeisung in die Eingangswelle 20 führt zu einem geringem radialen Bauraumbedarf. Zweckmäßigerweise sind entsprechende Dichtelemente mit geringen Leckageverlusten vorgesehen.As can be seen from FIG. 2, a pressure oil supply is ensured through an axial bore 68 of the first input shaft 20 . This pressure oil feed into the input shaft 20 leads to a small radial space requirement. Appropriate sealing elements with low leakage losses are expediently provided.

Kühlöl kann dabei axial über einen Ringspalt 70 dem Kupplungsgehäuse zugeführt werden. Eine radiale Durchströmung beider Kupplungen 16, 18 ist dadurch sichergestellt.Cooling oil can be fed axially to the clutch housing via an annular gap 70 . A radial flow through both clutches 16 , 18 is thereby ensured.

In einen Kupplungsraum 72 tritt dabei über Bohrungen 74 in einem Kupplungsgehäuse 76 Kühlöl ein. Die Kupplungen 16, 18 leiten ein Motordrehmoment bevorzugt über Steckverzahnungen 78 auf die Eingangswellen 20, 22. Entsprechende Fliehölkompensationskammern 80 sind in den Kupplungen 16, 18 vorgesehen. Über eine Verzahnung am Kupplungsgehäuse 76 ist zweckmäßigerweise ein Antrieb einer nicht dargestellten Ölpumpe vorgesehen. Der Kupplungsraum 72 ist zweckmäßigerweise nach außen öldicht abgeschlossen. Cooling oil enters into a clutch space 72 through bores 74 in a clutch housing 76 . The clutches 16 , 18 conduct an engine torque, preferably via splines 78, to the input shafts 20 , 22 . Corresponding centrifugal oil compensation chambers 80 are provided in the couplings 16 , 18 . A gear of an oil pump, not shown, is expediently provided via a toothing on the clutch housing 76 . The coupling space 72 is expediently sealed oil-tight to the outside.

BezugszeichenlisteReference list

1010th

Antriebswelle
drive shaft

1212th

Schwingungsdämpfungssystem
Vibration damping system

1414

Antriebsaggregat
Drive unit

1616

Kupplung
clutch

1818th

Kupplung
clutch

2020th

als Vollwelle ausgebildeten, radial innen liegend angeordnete Eingangswelle
input shaft designed as a solid shaft and arranged radially on the inside

2222

als Hohlwelle ausgebildeten, radial außenliegend angeordnete Eingangswelle
input shaft designed as a hollow shaft and arranged radially on the outside

2424th

Zahnrad für 5. Gang
5th gear wheel

2626

Zahnrad für 1. Gang/Rückwärtsgang
Gear for 1st gear / reverse gear

2828

Zahnrad für 3. Gang
3rd gear wheel

3030th

5. Gang
5th gear

3232

1. Gang
1st gear

3434

3. Gang
3rd gear

3636

Zahnrad für 4./6. Gang
Gear for 4th / 6th gear

3838

Zahnrad für 2. Gang
Gear for 2nd gear

4040

4. Gang
4th gear

4242

2. Gang
2nd gear

4444

6. Gang
6th gear

4646

//

4646

a Rückwärtsgang
a reverse gear

4848

erste Nebenwelle
first countershaft

5050

Zahnrad der ersten Nebenwelle
Gear of the first auxiliary shaft

5252

zweite Nebenwelle
second auxiliary wave

5454

Zahnrad der zweiten Nebenwelle
Second secondary shaft gear

5555

Außenverzahnung des Gehäuses des Differentialgetriebes
External toothing of the housing of the differential gear

5656

dritte Nebenwelle/Rückwärtsgang
third countershaft / reverse gear

5757

Differentialgetriebe
Differential gear

5858

Zahnrad der dritten Nebenwelle/Rückwärtsgang
Third countershaft / reverse gear

5959

Gehäuse des Differentialgetriebes
Differential gearbox housing

6060

erste Schiebemuffe
first sliding sleeve

6262

zweite Schiebemuffe
second sliding sleeve

6464

dritte Schiebemuffe
third sliding sleeve

6666

vierte Schiebemuffe
fourth sliding sleeve

6868

axiale Bohrung
axial bore

7070

Ringspalt
Annular gap

7272

Kupplungsraum
Clutch compartment

7474

Bohrungen
Holes

7676

Kupplungsgehäuse
Clutch housing

7878

Steckverzahnungen
Splines

8080

Fliehölkompensationskammern
Centrifugal oil compensation chambers

Claims (18)

1. Doppelkupplungsgetriebe, insbesondere eines Kraftfahrzeuges, mit zwei konzentrisch zueinander angeordneten, mit einer Antriebswelle (10) verbundenen, wahlweise mit jeweils einer Kupplung (16, 18) verbindbaren Eingangswellen (20, 22) und einer ersten und einer zweiten Nebenwelle (48, 52), welchen jeweilige Zahnradsätze (30, 32, 34, 40, 42, 44, 46) mit Zahnrädern (24, 26, 28, 36, 38) für Vorwärtsgänge und wenigstens einem Rückwärtsgang zugeordnet sind, dadurch gekennzeichnet, daß für wenigstens zwei Gänge (40, 44 bzw. 42, 46), welche jeweils einer anderen Nebenwelle (48, 50) zugeordnet sind, eingangswellenseitig ein einziges Zahnrad (36 bzw. 26) vorgesehen ist.1. Double clutch transmission, in particular of a motor vehicle, with two input shafts ( 20 , 22 ) and a first and a second auxiliary shaft ( 48 , 52 ) arranged concentrically to one another and connected to a drive shaft ( 10 ), optionally connectable with one clutch ( 16 , 18 ) each ), which respective gear sets ( 30 , 32 , 34 , 40 , 42 , 44 , 46 ) with gear wheels ( 24 , 26 , 28 , 36 , 38 ) for forward gears and at least one reverse gear are assigned, characterized in that for at least two gears ( 40 , 44 and 42 , 46 ), which are each assigned to a different auxiliary shaft ( 48 , 50 ), a single gear wheel ( 36 or 26 ) is provided on the input shaft side. 2. Doppelkupplungsgetriebe nach Anspruch 1, dadurch gekennzeichnet, daß fünf Vorwärtsgänge (30, 32, 24, 40, 42, 44) vorgesehen sind, wobei für den vierten Gang (40) und den sechsten Gang (44) sowie für den Rückwärtsgang (58) und den ersten Gang (32) eingangswellenseitig jeweils ein einziges Zahnrad (36, 26) vorgesehen ist.2. Double clutch transmission according to claim 1, characterized in that five forward gears ( 30 , 32 , 24 , 40 , 42 , 44 ) are provided, being for the fourth gear ( 40 ) and the sixth gear ( 44 ) and for the reverse gear ( 58 ) and the first gear ( 32 ) on the input shaft side, a single gear ( 36 , 26 ) is provided. 3. Doppelkupplungsgetriebe nach Anspruch 2, dadurch gekennzeichnet, daß die Zahnräder (24, 26, 28, 36, 38) der Gänge auf den Getriebeeingangswellen (20, 22) in Richtung Antriebswelle (10) aufeinanderfolgend für den fünften Gang (30), den ersten Gang (32), den Rückwärtsgang (58), den dritten Gang (34), den vierten/sechsten Gang (40, 44) und den zweiten Gang (42) angeordnet sind.3. Double clutch transmission according to claim 2, characterized in that the gears ( 24 , 26 , 28 , 36 , 38 ) of the gears on the transmission input shafts ( 20 , 22 ) in the direction of the drive shaft ( 10 ) successively for the fifth gear ( 30 ) first gear ( 32 ), reverse gear ( 58 ), third gear ( 34 ), fourth / sixth gear ( 40 , 44 ) and second gear ( 42 ) are arranged. 4. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Radsätze (30, 32, 34, 58) für den ersten, dritten, fünften Gang und Rückwärtsgang einer als Vollwelle ausgebildeten Eingangswelle (20) zugeordnet sind.4. Double clutch transmission according to one of the preceding claims, characterized in that the wheel sets ( 30 , 32 , 34 , 58 ) for the first, third, fifth gear and reverse gear are assigned to an input shaft ( 20 ) designed as a solid shaft. 5. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Radsätze (40, 42, 44) für den zweiten, vierten, sechsten und einer als Hohlwelle ausgebildeten Eingangswelle (22) zugeordnet sind.5. Double clutch transmission according to one of the preceding claims, characterized in that the wheel sets ( 40 , 42 , 44 ) for the second, fourth, sixth and an input shaft designed as a hollow shaft ( 22 ) are assigned. 6. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der ersten Nebenwelle (48) der fünfte (30), der sechste (44) und der Rückwärtsgang (46) in dieser Reihenfolge in Richtung Antriebswelle (10) zugeordnet sind.6. Double clutch transmission according to one of the preceding claims, characterized in that the first auxiliary shaft ( 48 ), the fifth ( 30 ), the sixth ( 44 ) and the reverse gear ( 46 ) are assigned in this order in the direction of the drive shaft ( 10 ). 7. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der zweiten Nebenwelle (52) der erste (32), dritte (34), vierte (40) und zweite Gang (42) in dieser Reihenfolge in Richtung Antriebswelle (10) zugeordnet sind.7. Double clutch transmission according to one of the preceding claims, characterized in that the second auxiliary shaft ( 52 ) the first ( 32 ), third ( 34 ), fourth ( 40 ) and second gear ( 42 ) assigned in this order in the direction of the drive shaft ( 10 ) are. 8. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß für die Gangpaare erster/dritter Gang (32, 34), vierter/zweiter Gang (40, 42) sowie sechster Gang/ Rückwärtsgang (44, 46) jeweils eine gemeinsame Schiebemuffe (60, 62, 64) angeordnet ist, welche die genannten Gänge jeweils wahlweise schaltet.8. Double clutch transmission according to one of the preceding claims, characterized in that for the gear pairs first / third gear ( 32 , 34 ), fourth / second gear ( 40 , 42 ) and sixth gear / reverse gear ( 44 , 46 ) each have a common sliding sleeve ( 60 , 62 , 64 ) is arranged, which selectively switches the gears mentioned. 9. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß für den Rückwärtsgang (46) eine dritte Nebenwelle (56) vorgesehen ist.9. Double clutch transmission according to one of the preceding claims, characterized in that a third countershaft ( 56 ) is provided for the reverse gear ( 46 ). 10. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß für den fünften Gang (30) eine separate Schiebemuffe (66) vorgesehen ist.10. Double clutch transmission according to one of the preceding claims, characterized in that a separate sliding sleeve ( 66 ) is provided for the fifth gear ( 30 ). 11. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwei naß laufende Lamellenkupplungen (16, 18) radial zueinander angeordnet sind.11. Double clutch transmission according to one of the preceding claims, characterized in that two wet-running multi-plate clutches ( 16 , 18 ) are arranged radially to one another. 12. Doppelkupplungsgetriebe nach Anspruch 11, dadurch gekennzeichnet, daß die radial innenliegende Kupplung (16) oder die radial außen liegende Kupplung (18) als Anfahrkupplung ausgebildet ist.12. Double clutch transmission according to claim 11, characterized in that the radially inner clutch ( 16 ) or the radially outer clutch ( 18 ) is designed as a starting clutch. 13. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die als innenliegende Vollwelle ausgebildete Eingangswelle (20) mit einer axialen Bohrung (68) ausgebildet ist.13. Double clutch transmission according to one of the preceding claims, characterized in that the input shaft ( 20 ) designed as an internal solid shaft is formed with an axial bore ( 68 ). 14. Doppelkupplungsgetriebe nach Anspruch 13, dadurch gekennzeichnet, daß das Kupplungsgehäuse (76) mit einem Ringspalt (70) zum Getriebegehäuse ausgebildet ist.14. Double clutch transmission according to claim 13, characterized in that the clutch housing ( 76 ) is formed with an annular gap ( 70 ) to the transmission housing. 15. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kupplungen (16, 18) jeweils mit einer Eingangswelle (20, 22) über jeweilige Steckverzahnungen (78) verbunden sind.15. Double clutch transmission according to one of the preceding claims, characterized in that the couplings ( 16 , 18 ) are each connected to an input shaft ( 20 , 22 ) via respective splines ( 78 ). 16. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß in jeweiligen Kupplungskolben der Kupplungen (16, 18) eine Fliehkraftkompensation (80) vorgesehen ist.16. Double clutch transmission according to one of the preceding claims, characterized in that a centrifugal force compensation ( 80 ) is provided in the respective clutch piston of the clutches ( 16 , 18 ). 17. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß an einem Kupplungsgehäuse (76) eine Verzahnung zum Antrieb einer Ölpumpe vorgesehen ist. 17. Double clutch transmission according to one of the preceding claims, characterized in that a toothing for driving an oil pump is provided on a clutch housing ( 76 ). 18. Doppelkupplungsgetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Antriebswelle (10) ein Zweimassenschwingungsdämpfer (12) vorgeschaltet ist.18. Double clutch transmission according to one of the preceding claims, characterized in that the drive shaft ( 10 ) is preceded by a dual-mass vibration damper ( 12 ).
DE19821164A 1998-05-12 1998-05-12 Double clutch Expired - Lifetime DE19821164B4 (en)

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EP1367294A3 (en) * 1998-12-24 2004-02-04 DaimlerChrysler AG Toothed speed-changing gearing with two parallel transmission paths
EP1367293A3 (en) * 1998-12-24 2004-02-04 DaimlerChrysler AG Toothed speed-changing gearing with two parallel transmission paths
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