[go: up one dir, main page]

WO2008064639A1 - Combination of a sealing washer and a leaf spring drive disk - Google Patents

Combination of a sealing washer and a leaf spring drive disk Download PDF

Info

Publication number
WO2008064639A1
WO2008064639A1 PCT/DE2007/002044 DE2007002044W WO2008064639A1 WO 2008064639 A1 WO2008064639 A1 WO 2008064639A1 DE 2007002044 W DE2007002044 W DE 2007002044W WO 2008064639 A1 WO2008064639 A1 WO 2008064639A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque converter
plate
piston
converter according
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2007/002044
Other languages
German (de)
French (fr)
Inventor
Adam Uhler
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.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112007002702T priority Critical patent/DE112007002702A5/en
Publication of WO2008064639A1 publication Critical patent/WO2008064639A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H2045/002—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  comprising a clutch between prime mover and fluid gearing
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H2045/005—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  comprising a clutch between fluid gearing and the mechanical gearing unit
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0252—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a damper arranged on input side of the lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0257—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a pump adapted for use as a secondary mass of the damping system
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

  • the present invention relates generally to torque converters and, more particularly, to a torque converter having a combination of a gasket and a leaf spring driver disk.
  • FIG. 1 shows prior art torque converters 10 with three hydraulic passages leading into torque converter 10.
  • the torque converter 10 includes a converter cover 4 and a pin connected to the cover 4; which absorbs the torque from the engine.
  • the lid 4 includes a turbine 46 rotatable relative to the lid 4 and a stator 44 disposed between an impeller 40 and the turbine 46.
  • the lid 4 has a tubular impeller hub 16.
  • the impeller hub 16 is located at a distance from a stator shaft 8, which is toothed with the stator 44.
  • the turbine 46 is non-rotatably connected to a turbine hub 20 and the turbine hub 20 is connected to a drive shaft 14 via a damper 38 and a damper hub 62.
  • the torque converter 10 also includes a clutch piston 30 and clutch plates 6.
  • a clutch plate 6 is rotatable by leaf springs 64 having a welded plate 48 and another clutch plate 6 rotatably connected to the lid 4.
  • the three leading into the torque converter 10 channels are: between the impeller hub 16 and the stator shaft 8; between the stator shaft 8 and the drive shaft 14, and as a bore within the drive shaft 14th
  • the three hydraulic passages of the torque converter 10 allow the formation of a sealed piston chamber 12 which allows the clutch 60 to be engaged.
  • the piston 30 is usually from the converter cover 4 and of the Drive shaft 14 enclosed.
  • the piston 30 urges the clutch 60 against the turbine 46, which requires an axial stop for the converter clutch 60.
  • the welded plate 48 is made of thick steel sheet and is welded to the cover 4 of the torque converter 10.
  • An object of the present invention is to provide a hydraulic torque converter comprising: a cover, a drive plate driven by the cover, and a lockup clutch having a piston plate, the piston plate being disposed between the drive plate and the cover, and the piston plate and the drive plate define a hydraulic chamber for actuating the piston plate.
  • Fig. 1 illustrates the upper half of a longitudinal section through a torque converter according to the prior art, in which the piston from the converter cover and the drive shaft is enclosed.
  • Fig. 2 illustrates an embodiment of a torque converter according to the present invention.
  • Fig. 3 illustrates another embodiment of the present invention in which the converter clutch exerts pressure through the center of the drive shaft.
  • FIG. 2 is a cross-sectional view of a hydraulic torque converter 100 embodying the present invention.
  • the torque converter 100 has a cover 104 and a pin 102 connected to the cover 104.
  • the lid 104 has a tubular impeller hub 116. Inside the lid 104 is an impeller 140, a turbine 146 connected to a turbine hub 120, and a stator 144.
  • the impeller hub 116 is spaced from a stator shaft 108 intermeshed with the stator 144.
  • a drive input shaft 114 of the transmission is intermeshed with the turbine hub 120.
  • the stator shaft 108 is sealed against the turbine hub 120.
  • the lid 104 is also secured to a centering bushing 142, which in turn is secured to a leaf spring driver disk 110.
  • the torque converter 100 also includes a lock-up clutch 160 having a piston 130 and clutch plates 106 and a damper 138.
  • the piston 130 is sealed by a seal 132 against the leaf spring driver disk 110.
  • the piston 130 is also sealed with a seal 128 against the centering bushing 142.
  • the turbine hub 120 is sealed by a seal 122 against the leaf spring driver disk 110.
  • the centering bushing 142 is sealed against the drive shaft 114 by a seal 124.
  • the turbine hub 120 rotates with respect to the centering bushing 142, for example by means of an additional centering bushing, wherein the turbine hub 120 can bypass an additional centering bushing 126.
  • the centering bush 142 also has at least one opening 142 between the stator shaft 108 and the drive shaft 114 to a chamber 112 so that liquid from an actuating channel 109 can flow through.
  • the pressure chamber 112 is a sealed pressure chamber and serves to actuate the piston 130.
  • the outer diameter of the chamber 112 is sealed by a seal 132 between the piston plate 130 and the leaf spring drive plate 110.
  • the engine torque for example, from an internal combustion engine via the pin 102 in the torque converter 100.
  • the torque is transmitted from the pin 102 to the cover 104.
  • the torque can be transmitted from the cover 104 to the impeller 140 and via the centering bushing 142 to the leaf spring drive plate 110.
  • a cooling fluid flows through the interior of the drive shaft and exits between the stator shaft 108 and the impeller hub 116.
  • the oil flows through the centering 126.
  • the bearing does not seal the chamber at any point.
  • Advantages of the present invention include less complexity of construction of the three channels by a sealed piston, a turbine damper, and a high slip capacity clutch. Due to the structural design can be dispensed with the welding of the clutch plate inside the lid and a saving of material and / or the number of parts can be achieved.
  • FIG. 3 shows another embodiment of the present invention. Similar to FIG. 2, FIG. 3 shows a cross section through a hydraulic torque converter 200.
  • the torque converter 200 has a cover 204 which is connected to a journal 202.
  • the lid 204 has a sealing seat 250.
  • Inside the lid 204 are an impeller 240, a turbine 246 with a turbine housing 248 and a stator 244.
  • the impeller hub 216 is spaced from a stator shaft 208 and a drive shaft 214.
  • a turbine hub 220 is fixedly secured to the housing 248 to create a liquid-tight seal.
  • the turbine housing 220 is sealed by a seal 218 against the stator shaft 208, thus creating a pressure chamber 212.
  • the torque converter 200 also includes a converter clutch 260 having a piston 230, clutch plates 206 and a damper 238.
  • the piston 230 is sealed by a seal 232 against the leaf spring driver disk.
  • the turbine hub 220 is sealed by a seal 222 against the leaf spring driver disk.
  • the engine torque passes through the pin 202 in the torque converter 200.
  • the torque is transmitted from the pin 202 to the cover 204. From the cover 204, the torque can be transmitted to the impeller 240 and to the leaf spring driver disk 210.
  • the cooling liquid enters through the actuating passage 209 between the stator shaft 208 and the drive shaft 214.
  • the coolant passes through a through-drilled hole 252 in a chamber 256.
  • the coolant exits between the stator shaft 208 and the impeller hub 216 again.
  • the actuating fluid flows through the interior of the drive shaft 214.
  • the pressure is passed through a transversely drilled hole in the sealing seat 250 in the pressure chamber 212.
  • the drilled through hole 254 lies in a different plane of rotation than the transversely drilled hole 252.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Fluid Gearings (AREA)
  • Mechanical Operated Clutches (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

The invention relates to a hydraulic torque converter which comprises a housing containing a drive disk driven by the housing and a lock-up clutch having a piston plate, said piston plate being interposed between the drive disk and the housing and the piston plate and the drive disk defining a hydraulic chamber for actuating the piston plate.

Description

Kombination aus einer Dichtungsscheibe und einer Blattfeder-Mitnehmerscheibe Combination of a sealing washer and a leaf spring driving disc

Die vorliegende Erfindung betrifft im Allgemeinen Drehmomentwandler und im Besonderen einen Drehmomentwandler mit einer Kombination aus einer Dichtungsscheibe und einer Blattfeder-Mitnehmerscheibe.The present invention relates generally to torque converters and, more particularly, to a torque converter having a combination of a gasket and a leaf spring driver disk.

HINTERGRUND DER ERFINDUNGBACKGROUND OF THE INVENTION

Fig. 1 zeigten Drehmomentwandler 10 nach dem Stand der Technik mit drei in den Drehmomentwandler 10 führenden hydraulischen Kanälen. Der Drehmomentwandler 10 beinhaltet einen Wandlerdeckel 4 und einen mit dem Deckel 4 verbundenen Zapfen; der das Drehmoment vom Motor aufnimmt. Der Deckel 4 schließt eine Turbine 46, die gegenüber dem Deckel 4 drehbar ist, und einen zwischen einem Laufrad 40 und der Turbine 46 angeordneten Stator 44 ein. Der Deckel 4 weist eine röhrenförmige Laufradnabe 16 auf. Die Laufradnabe 16 befindet sich in einem Abstand von einer Statorwelle 8, die mit dem Stator 44 verzahnt ist. Die Turbine 46 ist nichtdrehbar mit einer Turbinennabe 20 und die Turbinennabe 20 über einen Dämpfer 38 und eine Dämpfernabe 62 mit einer Antriebswelle 14 verbunden. Wenn der Dämpfer 38 zusammengedrückt wird, kommt es zu einer Relativbewegung zwischen der Turbinennabe 20 und der Dämpfernabe 62. Der Drehmomentwandler 10 beinhaltet auch einen Kupplungskolben 30 und Kupplungslamellen 6. Eine Kupplungslamelle 6 ist durch Blattfedern 64 drehbar mit einer angeschweißten Platte 48 und eine andere Kupplungslamelle 6 drehbar mit dem Deckel 4 verbunden. Die drei in den Drehmomentwandler 10 führenden Kanäle befinden sich: zwischen der Laufradnabe 16 und der Statorwelle 8; zwischen der Statorwelle 8 und der Antriebswelle 14, und als Bohrung innerhalb der Antriebswelle 14.FIG. 1 shows prior art torque converters 10 with three hydraulic passages leading into torque converter 10. The torque converter 10 includes a converter cover 4 and a pin connected to the cover 4; which absorbs the torque from the engine. The lid 4 includes a turbine 46 rotatable relative to the lid 4 and a stator 44 disposed between an impeller 40 and the turbine 46. The lid 4 has a tubular impeller hub 16. The impeller hub 16 is located at a distance from a stator shaft 8, which is toothed with the stator 44. The turbine 46 is non-rotatably connected to a turbine hub 20 and the turbine hub 20 is connected to a drive shaft 14 via a damper 38 and a damper hub 62. When the damper 38 is compressed, there is relative movement between the turbine hub 20 and the damper hub 62. The torque converter 10 also includes a clutch piston 30 and clutch plates 6. A clutch plate 6 is rotatable by leaf springs 64 having a welded plate 48 and another clutch plate 6 rotatably connected to the lid 4. The three leading into the torque converter 10 channels are: between the impeller hub 16 and the stator shaft 8; between the stator shaft 8 and the drive shaft 14, and as a bore within the drive shaft 14th

Die Vorteile nach dem aktuellen Stand der Technik bestehen in der Fähigkeit der Kanäle zum Steuern von drei Drücken innerhalb des Drehmomentwandlers 10, um Kupplungen einzukuppeln, auszukuppeln und zu kühlen. Die Nachteile dieser Kupplung besteht jedoch in der komplexen Konstruktion mit den drei Kanälen.The advantages of the current state of the art are the ability of the channels to control three pressures within the torque converter 10 to engage, disengage, and cool clutches. The disadvantages of this coupling, however, is the complex construction with the three channels.

Die drei hydraulischen Kanäle des Drehmomentwandlers 10 ermöglichen die Bildung einer abgeschlossenen Kolbenkammer 12, welche das Einkuppeln der Wandlerkupplung 60 ermöglicht. Der Kolben 30 ist üblicherweise vom Wandlerdeckel 4 und von der Antriebswelle 14 umschlossen. Der Kolben 30 drückt die Kupplung 60 gegen die Turbine 46, die für die Wandlerkupplung 60 einen axialen Anschlag benötigt. Die angeschweißte Platte 48 besteht aus dickem Stahlblech und ist am Deckel 4 des Drehmomentwandlers 10 angeschweißt.The three hydraulic passages of the torque converter 10 allow the formation of a sealed piston chamber 12 which allows the clutch 60 to be engaged. The piston 30 is usually from the converter cover 4 and of the Drive shaft 14 enclosed. The piston 30 urges the clutch 60 against the turbine 46, which requires an axial stop for the converter clutch 60. The welded plate 48 is made of thick steel sheet and is welded to the cover 4 of the torque converter 10.

ZUSAMMENFASSUNG DER ERFINDUNGSUMMARY OF THE INVENTION

Eine Aufgabe der vorliegenden Erfindung besteht darin, einen hydraulischen Drehmomentwandler bereitzustellen, der Folgendes umfasst: einen Deckel, eine durch den Deckel angetriebene Mitnehmerscheibe und eine Überbrückungskupplung mit einem Kolbenblech, wobei das Kolbenblech zwischen der Mitnehmerscheibe und dem Deckel angeordnet ist und das Kolbenblech und die Mitnehmerscheibe eine Hydraulikkammer zum Betätigen des Kolbenblechs definieren.An object of the present invention is to provide a hydraulic torque converter comprising: a cover, a drive plate driven by the cover, and a lockup clutch having a piston plate, the piston plate being disposed between the drive plate and the cover, and the piston plate and the drive plate define a hydraulic chamber for actuating the piston plate.

KURZBESCHREIBUNG DER ZEICHNUNGENBRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 veranschaulicht die obere Hälfte eines Längsschnitts durch einen Drehmomentwandler nach dem Stand der Technik, bei dem der Kolben vom Wandlerdeckel und von der Antriebswelle umschlossen ist.Fig. 1 illustrates the upper half of a longitudinal section through a torque converter according to the prior art, in which the piston from the converter cover and the drive shaft is enclosed.

Weitere Merkmale und Vorteile der Erfindung werden aus der folgenden detaillierten Beschreibung in Verbindung mit den beiliegenden Zeichnungen klar, wobei:Further features and advantages of the invention will be apparent from the following detailed description taken in conjunction with the accompanying drawings, in which:

Fig. 2 eine Ausführungsart eines Drehmomentwandlers gemäß der vorliegenden Erfindung veranschaulicht.Fig. 2 illustrates an embodiment of a torque converter according to the present invention.

Fig. 3 eine weitere Ausführungsart der vorliegenden Erfindung veranschaulicht, bei der die Wandlerkupplung durch die Mitte der Antriebswelle einen Druck ausübt.Fig. 3 illustrates another embodiment of the present invention in which the converter clutch exerts pressure through the center of the drive shaft.

DETAILLIERTE BESCHREIBUNG DER ERFINDUNGDETAILED DESCRIPTION OF THE INVENTION

Fig. 2 zeigt einen Querschnitt durch einen hydraulischen Drehmomentwandler 100, der die vorliegende Erfindung verkörpert. Der Drehmomentwandler 100 weist einen Deckel 104 und einen mit dem Deckel 104 verbundenen Zapfen 102 auf. Der Deckel 104 weist eine röhrenförmige Laufradnabe 116 auf. Im Innern des Deckels 104 befinden sich ein Laufrad 140, eine mit einer Turbinennabe 120 verbundene Turbine 146 und ein Stator 144. Die Laufradnabe 116 befindet sich in einem Abstand von einer mit dem Stator 144 verzahnten Statorwelle 108. Eine Antriebswelle 114 des Getriebes ist mit der Turbinennabe 120 verzahnt 121. Die Statorwelle 108 ist gegen die Turbinennabe 120 abgedichtet. Der Deckel 104 ist auch an einer Zentrierbuchse 142 befestigt, die wiederum an einer Blattfeder-Mitnehmerscheibe 110 befestigt ist.FIG. 2 is a cross-sectional view of a hydraulic torque converter 100 embodying the present invention. The torque converter 100 has a cover 104 and a pin 102 connected to the cover 104. The lid 104 has a tubular impeller hub 116. Inside the lid 104 is an impeller 140, a turbine 146 connected to a turbine hub 120, and a stator 144. The impeller hub 116 is spaced from a stator shaft 108 intermeshed with the stator 144. A drive input shaft 114 of the transmission is intermeshed with the turbine hub 120. The stator shaft 108 is sealed against the turbine hub 120. The lid 104 is also secured to a centering bushing 142, which in turn is secured to a leaf spring driver disk 110.

Der Drehmomentwandler 100 weist auch eine Überbrückungskupplung 160 auf, die einen Kolben 130 und Kupplungslamellen 106 und einen Dämpfer 138 aufweist. Der Kolben 130 ist durch eine Dichtung 132 gegen die Blattfeder-Mitnehmerscheibe 110 abgedichtet. Der Kolben 130 ist mit einer Dichtung 128 auch gegen die Zentrierbuchse 142 abgedichtet. Die Turbinennabe 120 ist durch eine Dichtung 122 gegen die Blattfeder-Mitnehmerscheibe 110 abgedichtet. Die Zentrierbuchse 142 ist durch eine Dichtung 124 gegen die Antriebsweile 114 abgedichtet. Die Turbinennabe 120 dreht sich gegenüber der Zentrierbuchse 142, zum Beispiel mittels einer zusätzlichen Zentrierbuchse, wobei die Turbinennabe 120 ein zusätzliches Zentrierlager 126 umgehen kann. Die Zentrierbuchse 142 weist auch mindestens eine Öffnung 142 zwischen der Statorwelle 108 und der Antriebswelle 114 zu einer Kammer 112 auf, damit Flüssigkeit von einem Betätigungskanal 109 durchfließen kann. Die Druckkammer 112 ist eine abgeschlossene Druckkammer und dient zur Betätigung des Kolbens 130. Der Außendurchmesser der Kammer 112 ist durch eine Dichtung 132 zwischen dem Kolbenblech 130 und der Blattfeder-Mitnehmerscheibe 110 abgedichtet.The torque converter 100 also includes a lock-up clutch 160 having a piston 130 and clutch plates 106 and a damper 138. The piston 130 is sealed by a seal 132 against the leaf spring driver disk 110. The piston 130 is also sealed with a seal 128 against the centering bushing 142. The turbine hub 120 is sealed by a seal 122 against the leaf spring driver disk 110. The centering bushing 142 is sealed against the drive shaft 114 by a seal 124. The turbine hub 120 rotates with respect to the centering bushing 142, for example by means of an additional centering bushing, wherein the turbine hub 120 can bypass an additional centering bushing 126. The centering bush 142 also has at least one opening 142 between the stator shaft 108 and the drive shaft 114 to a chamber 112 so that liquid from an actuating channel 109 can flow through. The pressure chamber 112 is a sealed pressure chamber and serves to actuate the piston 130. The outer diameter of the chamber 112 is sealed by a seal 132 between the piston plate 130 and the leaf spring drive plate 110.

Das Motordrehmoment gelangt zum Beispiel von einem Verbrennungsmotor über den Zapfen 102 in den Drehmomentwandler 100. Das Drehmoment wird vom Zapfen 102 zum Deckel 104 übertragen. Das Drehmoment kann vom Deckel 104 zum Laufrad 140 und über die Zentrierbuchse 142 zur Blattfeder-Mitnehmerscheibe 110 übertragen werden. Eine Kühlflüssigkeit fließt durch das Innere der Antriebswelle und tritt zwischen der Statorwelle 108 und der Laufradnabe 116 aus.The engine torque, for example, from an internal combustion engine via the pin 102 in the torque converter 100. The torque is transmitted from the pin 102 to the cover 104. The torque can be transmitted from the cover 104 to the impeller 140 and via the centering bushing 142 to the leaf spring drive plate 110. A cooling fluid flows through the interior of the drive shaft and exits between the stator shaft 108 and the impeller hub 116.

Zum Schließen der Kupplung 160 fließt Öl durch den Betätigungskanal 109 hinter dem Zahnkranz 121 der Turbinennabe, dem Lager 126, durch die Löcher 143 zur Kammer 112, um den Kolben 130 einzurücken. Der Kolben 130 drückt die Kupplungslamellen 106 gegen den Deckel 104, um das Drehmoment zum Dämpfer 138 zu übertragen. Zum Ausrücken des Kupplungskolbens 160 wird der Druck in der Kammer 112 über den - A -To close the clutch 160, oil flows through the actuation passage 109 behind the ring gear 121 of the turbine hub, the bearing 126, through the holes 143 to the chamber 112 to engage the piston 130. The piston 130 presses the clutch plates 106 against the cover 104 to transmit the torque to the damper 138. To disengage the clutch piston 160, the pressure in the chamber 112 over the - A -

Betätigungskanal 109 zwischen der Statorwelle 108 und der Antriebswelle 114 abgebaut. Das Öl fließt durch das Zentrierlager 126. Je nach konstruktiver Gestaltung kann auf das Zentrierlager 126 verzichtet werden. Das Lager dichtet die Kammer an keiner Stelle ab.Actuating channel 109 between the stator shaft 108 and the drive shaft 114 degraded. The oil flows through the centering 126. Depending on the structural design can be dispensed with the centering 126. The bearing does not seal the chamber at any point.

Zu den Vorteilen der vorliegenden Erfindung gehören eine geringere Komplexität der Konstruktion der drei Kanäle durch einen abgedichteten Kolben, einen Turbinendämpfer und eine Kupplung mit hoher Schlupfkapazität. Durch die konstruktive Gestaltung kann auf das Anschweißen der Kupplungslamelle im Innern des Deckels verzichtet und eine Einsparung an Material und/oder der Anzahl der Teile erreicht werden.Advantages of the present invention include less complexity of construction of the three channels by a sealed piston, a turbine damper, and a high slip capacity clutch. Due to the structural design can be dispensed with the welding of the clutch plate inside the lid and a saving of material and / or the number of parts can be achieved.

Fig. 3 zeigt eine weitere Ausführungsart der vorliegenden Erfindung. Fig. 3 zeigt ähnlich wie Fig. 2 einen Querschnitt durch einen hydraulischen Drehmomentwandler 200. Der Drehmomentwandler 200 weist einen Deckel 204 auf, der mit einem Zapfen 202 verbunden ist. Der Deckel 204 weist einen Dichtsitz 250 auf. Im Innern des Deckels 204 befinden sich ein Laufrad 240, eine Turbine 246 mit einem Turbinengehäuse 248 und ein Stator 244. Die Laufradnabe 216 befindet sich in einem Abstand von einer Statorwelle 208 und einer Antriebswelle 214. Eine Turbinennabe 220 ist fest mit dem Gehäuse 248 vernietet, um eine flüssigkeitsdichte Abdichtung zu erzeugen. Das Turbinengehäuse 220 ist durch eine Dichtung 218 gegen die Statorwelle 208 abgedichtet und erzeugt so eine Druckkammer 212.Fig. 3 shows another embodiment of the present invention. Similar to FIG. 2, FIG. 3 shows a cross section through a hydraulic torque converter 200. The torque converter 200 has a cover 204 which is connected to a journal 202. The lid 204 has a sealing seat 250. Inside the lid 204 are an impeller 240, a turbine 246 with a turbine housing 248 and a stator 244. The impeller hub 216 is spaced from a stator shaft 208 and a drive shaft 214. A turbine hub 220 is fixedly secured to the housing 248 to create a liquid-tight seal. The turbine housing 220 is sealed by a seal 218 against the stator shaft 208, thus creating a pressure chamber 212.

Der Drehmomentwandler 200 beinhaltet auch eine Wandlerkupplung 260 mit einem Kolben 230, Kupplungslamellen 206 und einem Dämpfer 238. Der Kolben 230 ist durch eine Dichtung 232 gegen die Blattfeder-Mitnehmerscheibe abgedichtet. Die Turbinennabe 220 ist durch eine Dichtung 222 gegen die Blattfeder-Mitnehmerscheibe abgedichtet.The torque converter 200 also includes a converter clutch 260 having a piston 230, clutch plates 206 and a damper 238. The piston 230 is sealed by a seal 232 against the leaf spring driver disk. The turbine hub 220 is sealed by a seal 222 against the leaf spring driver disk.

Das Motordrehmoment gelangt über den Zapfen 202 in den Drehmomentwandler 200. Das Drehmoment wird vom Zapfen 202 zum Deckel 204 übertragen. Vom Deckel 204 kann das Drehmoment zum Laufrad 240 und zur Blattfeder-Mitnehmerscheibe 210 übertragen werden. Die Kühlflüssigkeit tritt durch den Betätigungskanal 209 zwischen der Statorwelle 208 und der Antriebswelle 214 ein. Die Kühlflüssigkeit gelangt durch ein quer durchgebohrtes Loch 252 in eine Kammer 256. Die Kühlflüssigkeit tritt zwischen der Statorwelle 208 und der Laufradnabe 216 wieder aus. Zum Betätigen der Kupplung 260 fließt die Betätigungsflüssigkeit durch das Innere der Antriebswelle 214. Der Druck wird durch ein quer durchgebohrtes Loch im Dichtsitz 250 in die Druckkammer 212 geleitet. Das quer durchgebohrte Loch 254 liegt in einer anderen Rotationsebene als das quer durchgebohrte Loch 252. The engine torque passes through the pin 202 in the torque converter 200. The torque is transmitted from the pin 202 to the cover 204. From the cover 204, the torque can be transmitted to the impeller 240 and to the leaf spring driver disk 210. The cooling liquid enters through the actuating passage 209 between the stator shaft 208 and the drive shaft 214. The coolant passes through a through-drilled hole 252 in a chamber 256. The coolant exits between the stator shaft 208 and the impeller hub 216 again. To actuate the clutch 260, the actuating fluid flows through the interior of the drive shaft 214. The pressure is passed through a transversely drilled hole in the sealing seat 250 in the pressure chamber 212. The drilled through hole 254 lies in a different plane of rotation than the transversely drilled hole 252.

Claims

Ansprüche claims 1. Hydraulischer Drehmomentwandler, der Folgendes umfasst:A hydraulic torque converter comprising: einen Deckel, eine durch den Deckel angetriebene Mitnehmerscheibe; und eine Überbrückungskupplung mit einem Kolbenblech, wobei das Kolbenblech zwischen der Mitnehmerscheibe und dem Deckel angeordnet ist und dasa lid, a drive plate driven by the lid; and a lockup clutch with a piston plate, wherein the piston plate between the drive plate and the cover is arranged and the Kolbenblech und die Mitnehmerscheibe eine Hydraulikkammer zum Betätigen desPiston plate and the drive plate a hydraulic chamber for actuating the Kolbenblechs definieren.Defining the piston plate. 2. Hydraulischer Drehmomentwandler nach Anspruch 1 , der ferner eine Turbine und einen Dämpfer umfasst, wobei der Dämpfer zwischen der Mitnehmerscheibe und der Turbine angeordnet ist.2. A hydraulic torque converter according to claim 1, further comprising a turbine and a damper, wherein the damper between the drive plate and the turbine is arranged. 3. Hydraulischer Drehmomentwandler nach Anspruch 1 , der ferner eine Zentrierbuchse umfasst, die an der Mitnehmerscheibe und am Deckel befestigt ist.3. A hydraulic torque converter according to claim 1, further comprising a centering bushing which is secured to the drive plate and the cover. 4. Hydraulischer Drehmomentwandler nach Anspruch 1 , bei dem das Kolbenblech gegen die Mitnehmerscheibe abgedichtet ist.4. A hydraulic torque converter according to claim 1, wherein the piston plate is sealed against the drive plate. 5. Hydraulischer Drehmomentwandler nach Anspruch 3, bei dem die Zentrierbuchse mindestens eine Öffnung aufweist.5. A hydraulic torque converter according to claim 3, wherein the centering bush has at least one opening. 6. Hydraulischer Drehmomentwandler nach Anspruch 1 , bei dem ein Außendurchmesser der Kammer zwischen dem Kolbenblech und der Mitnehmerscheibe abgedichtet ist.6. A hydraulic torque converter according to claim 1, wherein an outer diameter of the chamber between the piston plate and the drive plate is sealed. 7. Hydraulischer Drehmomentwandler nach Anspruch 1, bei dem die Mitnehmerscheibe eine Blattfeder-Mitnehmerscheibe ist.7. A hydraulic torque converter according to claim 1, wherein the drive plate is a leaf spring drive plate. 8. Hydraulischer Drehmomentwandler nach Anspruch 1 , der ferner einen mit einer Statorwelle verzahnten Stator und eine mit einer Antriebswelle verzahnte Turbinennabe umfasst, wobei die Hydraulikkammer über eine Flüssigkeit mit einem Betätigungskanal zwischen der Statorwelle und der Antriebswelle verbunden ist. 8. A hydraulic torque converter according to claim 1, further comprising a geared to a stator shaft stator and a toothed with a drive shaft turbine hub, wherein the hydraulic chamber is connected via a liquid with an actuating channel between the stator shaft and the drive shaft. 9. Hydraulischer Drehmomentwandler nach Anspruch 1, bei dem die Turbinennabe mit einer Antriebswelle verzahnt und die Hydraulikkammer über eine Flüssigkeit mit einer Innenseite der Antriebswelle verbunden ist. 9. A hydraulic torque converter according to claim 1, wherein the turbine hub geared to a drive shaft and the hydraulic chamber is connected via a liquid with an inner side of the drive shaft.
PCT/DE2007/002044 2006-11-29 2007-11-13 Combination of a sealing washer and a leaf spring drive disk Ceased WO2008064639A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002702T DE112007002702A5 (en) 2006-11-29 2007-11-13 Combination of a sealing washer and a leaf spring driving disc

Applications Claiming Priority (16)

Application Number Priority Date Filing Date Title
DE102006056299 2006-11-29
DE102006056299.2 2006-11-29
US87410406P 2006-12-11 2006-12-11
US60/874,104 2006-12-11
DE102006061553 2006-12-27
DE102006061541 2006-12-27
DE102006061553.0 2006-12-27
DE102006061552.2 2006-12-27
DE102006061541.7 2006-12-27
DE102006061552 2006-12-27
US93423507P 2007-06-12 2007-06-12
US60/934,235 2007-06-12
US96277207P 2007-07-31 2007-07-31
US60/962,772 2007-07-31
US96485507P 2007-08-15 2007-08-15
US60/964,855 2007-08-15

Publications (1)

Publication Number Publication Date
WO2008064639A1 true WO2008064639A1 (en) 2008-06-05

Family

ID=39156613

Family Applications (4)

Application Number Title Priority Date Filing Date
PCT/DE2007/002046 Ceased WO2008064641A1 (en) 2006-11-29 2007-11-13 Power transmission device
PCT/DE2007/002044 Ceased WO2008064639A1 (en) 2006-11-29 2007-11-13 Combination of a sealing washer and a leaf spring drive disk
PCT/DE2007/002045 Ceased WO2008064640A1 (en) 2006-11-29 2007-11-13 Multifunctional torque converter for disconnecting the turbine from the idling engine and control method for disconnecting a multifunctional torque converter from the idling engine
PCT/DE2007/002043 Ceased WO2008064638A1 (en) 2006-11-29 2007-11-13 Power transmission device, especially multifunction converter unit

Family Applications Before (1)

Application Number Title Priority Date Filing Date
PCT/DE2007/002046 Ceased WO2008064641A1 (en) 2006-11-29 2007-11-13 Power transmission device

Family Applications After (2)

Application Number Title Priority Date Filing Date
PCT/DE2007/002045 Ceased WO2008064640A1 (en) 2006-11-29 2007-11-13 Multifunctional torque converter for disconnecting the turbine from the idling engine and control method for disconnecting a multifunctional torque converter from the idling engine
PCT/DE2007/002043 Ceased WO2008064638A1 (en) 2006-11-29 2007-11-13 Power transmission device, especially multifunction converter unit

Country Status (3)

Country Link
JP (3) JP5396627B2 (en)
DE (4) DE112007002702A5 (en)
WO (4) WO2008064641A1 (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5428820B2 (en) * 2009-12-11 2014-02-26 アイシン精機株式会社 Clutch device
WO2011110310A2 (en) * 2010-03-06 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Fluid coupling launch device
CN103228955B (en) 2010-11-24 2015-03-04 丰田自动车株式会社 Vehicular power transmission device
CN103228956B (en) 2010-11-24 2015-04-22 丰田自动车株式会社 Vehicle power transmission device
JP5594369B2 (en) 2010-11-24 2014-09-24 トヨタ自動車株式会社 Power transmission device for vehicle
CN103228954B (en) 2010-11-24 2015-02-25 丰田自动车株式会社 Vehicular power transmission device
RU2560197C1 (en) 2011-10-05 2015-08-20 Тойота Дзидося Кабусики Кайся Device decreasing vehicle vibration
JP5983146B2 (en) * 2012-07-24 2016-08-31 アイシン・エィ・ダブリュ株式会社 Starting device
DE102013224437A1 (en) * 2012-12-17 2014-06-18 Schaeffler Technologies Gmbh & Co. Kg torsional vibration dampers
CN103660910B (en) * 2013-12-06 2016-01-06 合肥工业大学 The hybrid power transmission system of the electric quiet liquid compound of a kind of oil
CN103770623B (en) * 2014-02-20 2016-03-02 合肥工业大学 The hybrid power transmission system of a kind of oil electricity and hydraulic pressure compound
DE102015215199A1 (en) * 2015-08-10 2017-02-16 Schaeffler Technologies AG & Co. KG Torque transfer device
US9822862B2 (en) * 2015-10-02 2017-11-21 Valeo Embrayages Hydrokinetic torque coupling device for a motor vehicle
US10041575B2 (en) 2015-12-18 2018-08-07 GM Global Technology Operations LLC Torsional damper system
DE102015226413A1 (en) * 2015-12-22 2017-06-22 Schaeffler Technologies AG & Co. KG Hybrid system for use in a hybrid vehicle
DE102015016938A1 (en) * 2015-12-24 2017-06-29 Daimler Ag A power train assembly

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325222A1 (en) * 2003-06-04 2004-12-23 Zf Friedrichshafen Ag Transducer bypass clutch for hydrodynamic torque converter, has spring washer that is connected at one end to support and at other end to piston
EP1672254A1 (en) * 2004-12-15 2006-06-21 Zf Friedrichshafen Ag Lockup clutch for hydrodynamic coupling

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1303614A (en) * 1961-08-03 1962-09-14 Franc Motor vehicle transmission
CS226877B1 (en) * 1981-09-15 1984-04-16 Antonin Ing Csc Hau Self-changing differential gearbox
FR2525312B1 (en) * 1982-04-20 1987-07-03 Valeo TRANSMISSION WITH HYDRAULIC COUPLING MEMBER AND LOCKING CLUTCH, PARTICULARLY FOR MOTOR VEHICLE
CS238524B1 (en) * 1983-12-29 1985-11-13 Olgert I Giruckij Hydromechanical gearbox
US4673071A (en) * 1984-11-28 1987-06-16 Aisin-Warner Limited Power delivery system
JP2655935B2 (en) * 1990-07-06 1997-09-24 本田技研工業株式会社 Multiple clutch structure and transmission using the multiple clutch structure
US5400884A (en) * 1992-05-14 1995-03-28 Kabushiki Kaisha Daikin Seisakusho Torque convertor
FR2709165B1 (en) * 1993-08-16 1995-10-13 Valeo Transmission with disengageable hydrokinetic coupling, especially for motor vehicles.
JPH07277014A (en) * 1994-04-15 1995-10-24 Motor Jidosha Kk Power transmission device between prime movers of compound prime mover for automobile
JPH07317873A (en) * 1994-05-20 1995-12-08 Hino Motors Ltd Hydraulic torque converter used in automobile
US5695028A (en) * 1995-02-23 1997-12-09 Exedy Corporation Torque converter having both a lock-up clutch and a disengaging clutch mechanism
JP3434383B2 (en) * 1995-03-14 2003-08-04 株式会社エクセディ Torque converter
JP3447141B2 (en) * 1995-04-07 2003-09-16 株式会社エクセディ Torque converter
JP3225810B2 (en) * 1995-08-10 2001-11-05 トヨタ自動車株式会社 Hydraulic clutch device with flywheel
JPH09280337A (en) * 1996-04-10 1997-10-28 Exedy Corp Continuously variable transmission
JP3781518B2 (en) * 1997-08-12 2006-05-31 富士重工業株式会社 Automatic transmission
DE19812686C1 (en) * 1998-03-23 1999-07-01 Mannesmann Sachs Ag Rotary motion converter
DE10005506A1 (en) * 2000-02-08 2001-08-09 Mannesmann Sachs Ag Hydrodynamic coupling has friction unit which can be controlled to vary its friction action which with regard to working pressure fluid prevailing in casing assembly is optionally adjustable between limiting value ranges
JP3952490B2 (en) * 2000-03-16 2007-08-01 マツダ株式会社 Hybrid vehicle travel control device
DE10117746B4 (en) * 2000-04-28 2017-06-29 Schaeffler Technologies AG & Co. KG Torque transfer device
FR2816019B1 (en) * 2000-11-02 2003-01-03 Valeo HYDROKINETIC COUPLING APPARATUS, PARTICULARLY FOR MOTOR VEHICLE
JP2004353789A (en) * 2003-05-29 2004-12-16 Honda Motor Co Ltd Double clutch device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325222A1 (en) * 2003-06-04 2004-12-23 Zf Friedrichshafen Ag Transducer bypass clutch for hydrodynamic torque converter, has spring washer that is connected at one end to support and at other end to piston
EP1672254A1 (en) * 2004-12-15 2006-06-21 Zf Friedrichshafen Ag Lockup clutch for hydrodynamic coupling

Also Published As

Publication number Publication date
DE112007003308A5 (en) 2009-10-29
JP2008138879A (en) 2008-06-19
JP5190641B2 (en) 2013-04-24
WO2008064640A1 (en) 2008-06-05
JP2008137650A (en) 2008-06-19
WO2008064641A1 (en) 2008-06-05
WO2008064638A1 (en) 2008-06-05
DE112007002702A5 (en) 2009-08-13
DE112007002624A5 (en) 2009-08-06
DE112007002623A5 (en) 2009-08-06
JP5396627B2 (en) 2014-01-22
JP2008138877A (en) 2008-06-19

Similar Documents

Publication Publication Date Title
WO2008064639A1 (en) Combination of a sealing washer and a leaf spring drive disk
EP1857700B1 (en) Clutch assembly
EP1608891B1 (en) Hydrodynamic converter comprising a primary clutch
DE19742586C2 (en) Gearbox for an auxiliary device
DE102011120776A1 (en) TORQUE TRANSDUCER WITH LOCKING COUPLING
EP1857698B1 (en) Coupling assembly
DE102008026426A1 (en) Hydrodynamic coupling device for use in vehicle transmission in motor vehicle i.e. hybrid vehicle, has pump and turbine located in housing, where turbine is in connection with pump, and chamber partially enclosed by housing and plate
DE4121586A1 (en) HYDRODYNAMIC TORQUE CONVERTER WITH COOLING OIL CIRCUIT
EP2129928B1 (en) Clutch arrangement
DE102007014311A1 (en) Hydrodynamic coupling device
DE4320288A1 (en) Gearbox for forward and reverse travel
DE102008020674A1 (en) Torque converter with flow arrangement for a cooling fluid and with an arrangement for transmitting torque to a damper
WO2004085884A2 (en) Hydrodynamic torque converter
EP1900971A1 (en) Hydrostatic/mechanical transmission
DE10228812A1 (en) coupling device
DE102008060940A1 (en) Transducer device i.e. motor vehicle transducer device, has operating channels crossed with each other once and shiftedly arranged to each other in circumferential direction, where operating channels are separated from each other
DE112012001865T5 (en) Friction element, clutch plate, clutch device and torque converter
EP1561961B1 (en) Mulitple clutch device
WO2008148512A1 (en) Torque transmission device
EP2626584B1 (en) hydraulic coupling
DE102012211675A1 (en) Clutch assembly for a transmission, and method for controlling a separating clutch
DE102008040171A1 (en) Clutch device e.g. dual clutch device, for arranging in drive train of e.g. land vehicle, has fluid-passages formed in side wall and/or in pot bases, where side wall connects tooth heads and tooth bottoms
DE102008020678A1 (en) Three-phase torque converter with sealed piston and forced cooling flow
DE102019128300B3 (en) Drive arrangement for a motor vehicle
DE102011050793B4 (en) Gearbox with controllable differential lock

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07846326

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 1120070027029

Country of ref document: DE

REF Corresponds to

Ref document number: 112007002702

Country of ref document: DE

Date of ref document: 20090813

Kind code of ref document: P

122 Ep: pct application non-entry in european phase

Ref document number: 07846326

Country of ref document: EP

Kind code of ref document: A1