WO2008104146A1 - Kraftübertragungsvorrichtung - Google Patents
Kraftübertragungsvorrichtung Download PDFInfo
- Publication number
- WO2008104146A1 WO2008104146A1 PCT/DE2008/000175 DE2008000175W WO2008104146A1 WO 2008104146 A1 WO2008104146 A1 WO 2008104146A1 DE 2008000175 W DE2008000175 W DE 2008000175W WO 2008104146 A1 WO2008104146 A1 WO 2008104146A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- power transmission
- coupling
- transmission device
- pressure
- clutch
- Prior art date
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
-
- 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
- F16H2045/0221—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
- F16H2045/0252—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 invention relates to a power transmission device having an input and an output, a hydrodynamic component arranged between input and output, comprising at least one primary wheel and one secondary wheel, and at least one shiftable clutch device.
- Power transmission devices disposed between a prime mover and a transmission assembly are known in a variety of prior art designs. These generally comprise an input and at least one output, wherein the input at least indirectly, that is directly or via further transmission elements with the drive motor can be coupled and at least one output connected to one of the power transmission device downstream transmission unit, usually a change gear is.
- a hydrodynamic component preferably in the form of a hydrodynamic speed / torque converter, is arranged. This comprises at least one designated in the power flow from the input to the output as the impeller first impeller and a turbine wheel referred to as a second impeller.
- a device in the form of a switchable coupling device acting as a bridging clutch is provided.
- the lock-up clutch serves the coupling between the input or the connection between the input and the impeller and the turbine wheel.
- the actuation takes place via an actuating device, which in the simplest case comprises an adjusting device in the form of a piston element.
- an actuating device which in the simplest case comprises an adjusting device in the form of a piston element.
- the hydrodynamic speed / torque converter or the entire power transmission device is designed as a two-channel or three-channel unit. When training in three-channel design while the actuator is subjected to a separately controllable pressure.
- the remaining pressure chambers in the power transmission device in particular the working space in the speed / torque converter and the space between the hydrodynamic speed / torque converter and the lock-up clutch and the adjusting device are then flowed through either centripetal or centrifugal, via the individual ports to the pressure chambers an external circuit adjusting flow circuit is generated in the hydrodynamic speed / torque converter for cooling purposes.
- the performance will be in a hydrodynamically transmitted operating range.
- the primary impeller acting as impeller is coupled directly to the engine and the turbine wheel to the output or the input of a downstream change gear.
- the lock-up clutch is activated and the power between the input and the output of the power transmission device mechanically bypassing the hydrodynamic power branch in a mechanical power branch transmitted.
- the power flow can be done alone on the individual power branches and power sharing on both together.
- the drive machine can be separated from the output by the lock-up clutch, but with filled hydrodynamic component, which is the case with the hydrodynamic speed / torque converter in the bridged state, here is still torque in the hydrodynamic component introduced, which results in idling the engine in power loss.
- torque shocks are introduced from the side of the output in the hydrodynamic component.
- a coupling device which serves for decoupling of the pump impeller and thus for decoupling the drive machine of a power transmission device downstream transmission unit.
- the impeller clutch is required only for this operating range.
- the impeller clutch requires its own control and is often arranged in an area that leads to increase the space in the radial or axial direction.
- the hydrodynamic component is still associated with the transmission assembly functionally via the connection to the turbine wheel.
- the invention is therefore the object of developing a power transmission device of the type mentioned in such a way that it is designed as a multi-functional unit, that is at least one further switchable coupling, and further the already known for power transmission devices three-channel principle is maintained and by a small size in the axial as well as radial direction is characterized.
- a power transmission device for use in drive trains, in particular of vehicles, with an input which can be coupled to a drive machine and at least one nem, with a subsequent power transmission unit coupled output, comprising a hydrodynamic component with at least one impeller and a turbine wheel, a housing and a switchable coupling device according to the invention is characterized in that the support of the switchable coupling device arranged in the axial direction on two sides of the coupling device and with a Pressure acted upon supporting elements to form a pressurizable means, the coupling parts receiving chamber takes place.
- the registered axial forces and axial stresses in the power transmission device can be kept low by the lack of a fixed support, which is reflected in the design of the components.
- the support elements are preferably guided to each other in a pressure-tight manner displaceable in the axial direction.
- the support elements may be designed differently depending on the arrangement and function of the switchable coupling device. At least one of the support elements is preferably formed to increase the functional concentration and reduce the number of components of a coupling part or a, a coupling part supporting element of another switchable coupling device.
- a device for damping vibrations with at least one primary part and a secondary part, which are rotatable coaxially to each other and circumferentially limited relative to each other, provided, preferably, a support element from the primary part or secondary part or with this rotatably coupled element is formed ,
- Another possible embodiment is the formation of the support element directly from the turbine wheel of the hydrodynamic component.
- At least one of the support elements is designed as a piston element, which partially takes over the function of the adjusting device.
- both support elements are designed as piston elements.
- both support elements are preferably arranged in the same chamber which can be acted upon with pressure medium and are subjected to the same pressure.
- the already existing ambient pressure of the switchable coupling device is used and a loosening or closing of the switchable coupling device is dependent solely on the pressure in the pressure chamber formed between the support elements.
- the support elements are acted upon by the pressure in the interior of the housing between the housing inner wall and the outer circumference of the hydrodynamic component.
- the switchable coupling device designed as a disc clutch comprising at least one, at least one disc-shaped element comprising the first coupling part and a at least one disc-shaped element comprising the second coupling part, which are at least indirectly operatively connected to each other via an actuating device, is acted upon by the acted upon with pressure medium chamber a pressure which is lower than the ambient pressure, the switchable coupling device closed and solved in excess of the pressure in the pressurizable medium pressure chamber by the ambient pressure, the switchable coupling device.
- the inventive actuation of a switchable coupling device and support on two support elements can be used for each switchable coupling device of a power transmission device, regardless of the function.
- the switchable coupling device with axial support according to the invention may be a device for bypassing the power flow via the hydrodynamic component, a turbine wheel clutch or an impeller clutch.
- Figure 1 illustrates in a schematic simplified representation in an axial section a
- FIG. 2 illustrates an embodiment according to FIG. 1 with indication of the pressure chambers.
- FIG. 1 shows a schematic simplified representation of the basic structure of a power transmission device 1 according to the invention comprising a hydrodynamic component 2 and a switchable clutch device 3.
- the power transmission device 1 further comprises at least one input 4 and at least one output 5, the input 4 being at least indirectly non-rotatable with a not shown here drive machine is connected in integration of the power transmission device 1 in a drive train.
- the output 5 is at least indirectly coupled to a unit in use of the power transmission device in the drive train of this downstream power transmission unit, for example in the form of a transmission.
- the output 5 is designed according to a particularly advantageous embodiment directly as a transmission input shaft.
- the hydrodynamic component 2 is arranged between input 4 and output 5 and comprises at least one impeller acting as pump impeller P in force flow direction from input E to output A and connected to input E and acting as turbine wheel T and at least indirectly coupled to output 5 another paddle wheel. If the hydrodynamic component 2 is preferably designed as a hydrodynamic speed / torque converter, at least one stator L is provided. This is preferably supported via a freewheel F on a stationary or a rotating element, here for example a support shaft 6 from.
- the hydrodynamic component 2 in the form of a hydrodynamic speed / torque converter allows a simultaneous conversion of speed and torque. This component is usually operated only with full filling. Partial filling conditions are also conceivable. Furthermore, an embodiment is conceivable free of a stator L.
- the power transmission device 1 further comprises means for at least partially bypassing the hydrodynamic power branch via the hydrodynamic component.
- This is preferably carried out in the form of a so-called lock-up clutch 7.
- This comprises at least a first and a second coupling part 7.1 and 7.2, which are at least indirectly rotatably engageable with each other in operative connection.
- the coupling parts 7.1 and 7.2 include in the execution of the lock-up clutch 7 as a switchable clutch in the form of a frictional clutch, in particular in the form of a multi-plate clutch, at least one lamella each.
- an adjusting device 8 for actuating the lock-up clutch 7, comprises a piston element 9 which can be acted upon with pressure medium.
- the piston member 9 is to pressure medium-tight and slidable in the axial direction to form a pressurizable means pressurized chamber 10 either at the entrance 4, in particular a non-rotatably coupled thereto element or output 5 out.
- the guide is at the output 5, here in the form of a hub 11.
- the operating means of the hydrodynamic component 2 is used in the simplest case.
- the input 4 is at least indirectly connected to the impeller P of the hydrodynamic component 2, in this case via a housing 12.
- the housing 12 is designed as a rotating housing and comprises at least one housing part 12.1, which is non-rotatably connected to the pump housing.
- wheel P is connected and is usually formed by the pump shell and a cover member 12.2 in the form of the second housing part.
- the leadership of the piston member 9 can be done directly on the housing 12, in particular the housing part 12.1 or rotatably connected to this element.
- the leadership of the piston member 9 in the region of its inner circumference 13 is carried out as already stated on the hub 11.
- the leadership is pressure and liquid-tight.
- a first operating range is characterized by the power transmission between input 4 and output 5 as viewed via the hydrodynamic component 2.
- the power transmission takes place essentially hydrodynamically.
- the second operating range is characterized by the bridging of the hydrodynamic power branch.
- the power transmission between the input 4 and the output 5 takes place via the bridging clutch 7, bypassing the hydrodynamic component 2 between the input 4 directly to the output 5, here the hub 11 and the transmission input shaft coupled thereto, which is designated here by 14.
- a device 15 for damping vibrations comprises a primary part 16 and a secondary part 17, the primary part and the secondary part 16, 17 being arranged coaxially with one another and being rotatable in the circumferential direction limited to one another.
- Primary part 16 and secondary part 17 are coupled to each other via means 18 for transmitting torque and means 19 for damping coupling.
- the means 18 for transmitting torque and the means 19 for damping coupling of one and the same components are formed.
- the device 15 for damping vibrations is respectively arranged downstream of the hydrodynamic component 2 and the lockup clutch 7 in the direction of force flow between the input 4 and the output 5. Concerning the actual execution there are a lot of possibilities, which are not discussed here.
- the switchable coupling device 3 which is designed here as a so-called turbine wheel clutch 20 and the idle shutdown of the hydrodynamic component 2 is used.
- This is arranged between the turbine wheel T and the output 5, in particular the transmission input shaft 14.
- This includes in the simplest case again a first coupling part 20.1 and a second coupling part 20.2, wherein the first coupling part 20.1 at least indirectly, that is indirectly, is rotatably connected here via the device 15 for damping vibrations with the hydrodynamic component 2, and here the Coupling takes place directly with the turbine wheel T.
- the second coupling part 20.2 is at least indirectly rotationally fixed, that is directly or indirectly connected to the output 5 rotatably.
- the power transmission device 1 is designed, for example, in a three-channel design with regard to the mode of operation of the hydrodynamic component 2 and the bypass clutch 7. This then comprises at least three ports, a first port 21 which is coupled to the pressurizable medium pressure chamber 10 for acting on the piston element 9, another port 22 which is connected to a working space 23 of the hydrodynamic component 2 and a third, not here port shown, which is coupled to a fillable with pressure medium space 25, which is formed between the adjusting device 8 of the lock-up clutch 7 and the outer periphery 26 of the hydrodynamic component 2 and thus the interior of the housing 12.
- the same pressure conditions exist in the pressure space 25 outside the hydrodynamic component, which is enclosed by the housing 12, as in the hydrodynamic component.
- the resource management in the hydrodynamic component 2 can be controlled via these connections, in particular the second connection 22 and the further third connection, that is to say between centrifugal and centripetal flow, and thus also an external cooling circuit can be maintained.
- the switchable coupling device 3 in the form of the turbine wheel 20 is inventively constructed such that the pressure can be set within this lower than the ambient pressure.
- the support of the switchable coupling device 3 takes place on two on both sides of the coupling device 3 arranged and acted upon by a pressure supporting elements A1, A2 to form a pressurizable means, the coupling parts 20.1, 20.2 recordable chamber 28.
- This chamber 28 is disposed in the chamber 25.
- the acted upon with pressure medium chamber 28 is here formed by a non-rotatably coupled to the secondary part 17 of the device for damping vibrations 15 and thus the turbine wheel T element and a piston element as actuator 29.
- the secondary part 17 of the device for damping vibrations 15 at the same time forms the support for the first coupling input part 20.1 and here carries, for example, the outer plates or is rotatably connected thereto.
- the second coupling part 20.2 is formed by an inner disk carrier, which is supported on the hub 11.
- the the switchable coupling device 3 associated piston member is pressure and liquid-tight with respect to the first coupling part 20.1 and the second coupling part 20.2 feasible, preferably the guide on this or a non-rotatably coupled thereto element to form a gap for receiving the lamellar arrangement.
- the first coupling part 20.1 is connected to this not only with the turbine wheel T rotatably, but also with respect to this and the second coupling part 20.2 pressure- and liquid-tight.
- the chamber 28 which can be acted upon by pressure medium is formed, to which a separate connection 30 is assigned.
- the pressure in the chamber 28 can be adjusted.
- the adjusting device 29, in particular the piston element and the first coupling part 20.1 form here the support elements A1, A2, which are acted upon by the pressure in the chamber 25 and thus the pressure in the designed as a converter hydrodynamic component 2.
- the pressure acts in the pressure medium can be acted upon space 25.
- the pressure on the adjusting device 29, in particular the end face 31 on the piston element 9 is greater than in the pressurized medium beauf ble chamber 28, that is inside the coupling means 3.
- the pressure must be equal to or greater than at the End face 31 and thus be acted upon by pressure medium chamber 25.
- the switchable coupling device 3 thus comprises no fixed stop.
- the slats of the switchable coupling device 3 are pressed by the adjusting device 29 against a plate, here the carrier of the first coupling part 20.1, on the back of the same pressure acts as on the piston.
- the clutch plates are almost between two piston elements, which are acted upon on both sides with the same pressure. If the switchable clutch device 3 is closed, the pressure between the two pistons is lowered or the pressure surrounding the clutch is increased.
- FIG. 2 illustrates the pressure chambers and propagation of the pressures for the embodiment according to FIG. It can be seen that the pressure chamber 28 is disposed within the pressure chamber 25, wherein on the pressure medium can be acted upon this space 28 forming walls, which are preferably formed directly on individual coupling elements, in particular coupling parts 20.1 and 20.2, while the pressure in the pressure medium acted upon chamber 25 acts.
- the application takes place at the mutually oppositely oriented wall areas and causes quasi a counterforce to the piston force, so that there is a balance between this and only when reducing the pressure in the pressure chamber 28, the switchable coupling device 3 can be closed.
- FIG. 1 The solution according to the invention is shown in FIG. 1 for a particularly advantageous application in the form of the turbine wheel clutch. It is also conceivable, however, the use not shown here as a switchable coupling 3 in the form of the lock-up clutch 7. Another age- native or additional possibility consists in the formation of a switchable coupling device 3 in the form of a so-called impeller clutch for switching off or decommissioning of the impeller from the prime mover.
- the individual options can also be combined with each other, in particular if it is a power transmission device 1, which is designed as a multifunction unit and has a plurality of switchable coupling devices, in particular additionally or optionally to the lock-up clutch further coupling devices in the form of a Pumpenrad- and / or Turbinenradkupplung.
- A1 support elements
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Of Transmissions (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112008000356T DE112008000356A5 (de) | 2007-02-27 | 2008-01-31 | Kraftübertragungsvorrichtung |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US90379507P | 2007-02-27 | 2007-02-27 | |
US60/903,795 | 2007-02-27 | ||
DE102007030718 | 2007-07-02 | ||
DE102007030718.9 | 2007-07-02 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008104146A1 true WO2008104146A1 (de) | 2008-09-04 |
Family
ID=39367614
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2008/000175 WO2008104146A1 (de) | 2007-02-27 | 2008-01-31 | Kraftübertragungsvorrichtung |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE112008000356A5 (de) |
WO (1) | WO2008104146A1 (de) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1303614A (fr) * | 1961-08-03 | 1962-09-14 | Franc | Transmission pour véhicule automobile |
US3537262A (en) * | 1969-02-26 | 1970-11-03 | Borg Warner | Transmission mechanism |
FR2557658A1 (fr) * | 1983-12-29 | 1985-07-05 | Ustav Pro Vyzkum Motorovych Vo | Boite hydromecanique de changement de vitesse |
FR2709165A1 (fr) * | 1993-08-16 | 1995-02-24 | Valeo | Transmission à accouplement hydrocinétique débrayable, notamment pour véhicules automobiles. |
US5699887A (en) * | 1995-03-10 | 1997-12-23 | Fichtel & Sachs Ag | Hydrokinetic torque converter with an impeller clutch and a bridge coupling |
-
2008
- 2008-01-31 WO PCT/DE2008/000175 patent/WO2008104146A1/de active Application Filing
- 2008-01-31 DE DE112008000356T patent/DE112008000356A5/de not_active Ceased
- 2008-01-31 DE DE102008007017A patent/DE102008007017A1/de not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1303614A (fr) * | 1961-08-03 | 1962-09-14 | Franc | Transmission pour véhicule automobile |
US3537262A (en) * | 1969-02-26 | 1970-11-03 | Borg Warner | Transmission mechanism |
FR2557658A1 (fr) * | 1983-12-29 | 1985-07-05 | Ustav Pro Vyzkum Motorovych Vo | Boite hydromecanique de changement de vitesse |
FR2709165A1 (fr) * | 1993-08-16 | 1995-02-24 | Valeo | Transmission à accouplement hydrocinétique débrayable, notamment pour véhicules automobiles. |
US5699887A (en) * | 1995-03-10 | 1997-12-23 | Fichtel & Sachs Ag | Hydrokinetic torque converter with an impeller clutch and a bridge coupling |
Also Published As
Publication number | Publication date |
---|---|
DE102008007017A1 (de) | 2008-08-28 |
DE112008000356A5 (de) | 2009-11-19 |
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