WO2008043331A1 - Force transmission device - Google Patents
Force transmission device Download PDFInfo
- Publication number
- WO2008043331A1 WO2008043331A1 PCT/DE2007/001653 DE2007001653W WO2008043331A1 WO 2008043331 A1 WO2008043331 A1 WO 2008043331A1 DE 2007001653 W DE2007001653 W DE 2007001653W WO 2008043331 A1 WO2008043331 A1 WO 2008043331A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- output
- power transmission
- transmission device
- hydrodynamic
- bearing
- 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
- 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
- F16H2045/007—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a damper between turbine of the 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
- F16H2045/0215—Details of oil circulation
-
- 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
- F16H2045/0273—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, in detail with the features of the preamble of claim 1.
- Power transmission devices for use in motor vehicles as a combined starting and bridging unit are known in a variety of designs. Representative reference is made here to the document DE 103 50 935 A1.
- This comprises a hydrodynamic component in the form of a hydrodynamic speed / torque converter, comprising a primary impeller functioning as impeller, which is connected at least indirectly non-rotatably to the input of the power transmission device and a secondary wheel functioning as a turbine wheel, which is connected at least indirectly to the output of the power transmission device.
- a device for bridging and thus bypassing the power flow via the hydrodynamic component is provided.
- This comprises, when designed as a friction clutch, a first friction surface arrangement, which is non-rotatably coupled to the input or the connection between the input and the impeller, and a second friction surface arrangement which can be brought into operative connection with the first friction surface arrangement via an actuating device.
- a device for damping vibrations is provided between the second friction surface arrangement and the output.
- This comprises a primary part and a secondary part, which are arranged coaxially to each other, limited in the circumferential direction relative to each other limited rotatable and connected to each other via means for transmitting torque and damping coupling.
- the secondary part is at least indirectly rotatably connected to the output. Indirectly non-rotatable means that the coupling takes place either directly or via intermediate elements.
- the turbine wheel of the hydrodynamic component is non-rotatably connected to the primary part of the device for damping vibrations.
- the power transmission device is designed here as a three-channel system. This means that, in addition to the two connections to the hydrodynamic speed / torque converter, a further connection is provided for acting on the actuating piston for the friction surface arrangements.
- actuation of the actuator and thus activation of the lock-up clutch forces are exerted due to the coupling between this and the device for damping vibrations, which generate uncontrollable friction conditions in the damper itself and / or the connecting elements. Forces that arise in or in the immediate vicinity of the lock-up clutch, lead to axial forces and radial forces on the device for damping of Vibrations.
- the invention is therefore based on the object, a power transmission device of the type mentioned in such a way that the mentioned disadvantages are avoided.
- the focus is on an embodiment of the storage of the device for damping vibrations free from uncontrollable foreign friction, which deformations of the damper components and wobbling movements should be largely excluded.
- the solution according to the invention should be characterized by a low design effort.
- a power transmission device in particular for use in vehicles, which is usually preceded by a transmission unit, comprises an input coupled to a drive, in particular an engine and an output, a hydrodynamic component, with at least one impeller and a turbine wheel, a device for Damping of vibrations with a primary part and a secondary part, which are rotatable in the circumferential direction limited relative to each other and a device for bypassing the power transmission via the hydrodynamic component.
- the secondary part and the turbine wheel are at least indirectly non-rotatably connected to the output.
- the device for bypassing, in particular bridging, the hydrodynamic component comprises a first friction surface arrangement at least indirectly coupled to the input and a second friction surface arrangement connected to the output, which can be brought into operative connection with one another via an actuating device.
- the second friction surface arrangement is non-rotatably connected to the primary part of the device for damping vibrations and primary and second Reib lakeanssen are mounted on a common bearing arrangement, wherein the bearing assembly is disposed axially between the device for bypassing the hydrodynamic component and the device for damping vibrations.
- the bearing assembly comprises at least one axial or radial bearing.
- the bearing arrangement in the axial direction between the input and output viewed within the axial extent of the lock-up clutch and the device for damping vibrations is arranged or in the axial direction between the input and output of the power transmission between lock-up clutch and the Device for damping vibrations.
- the bearing arrangement is characterized by both a radial and axial support effect and comprises for this purpose at least one combined axial-radial bearing.
- the arrangement of the bearing assembly has the advantage that axial forces from the means for bridging the hydrodynamic component, in particular the lock-up clutch in the direction of the device for damping vibrations directly at the output or on a rotatably coupled to the output element to the turbine hub and / or whose thrust bearing can be supported. Furthermore, deformations and additional loads in the device for damping vibrations are avoided by this type of power flow in the direction of the axis of rotation.
- the radial bearing in close proximity to the lock-up clutch allows only slight tilting, which in turn leads to reduced controlled friction and less tumbling.
- the bearing assembly is designed as a sliding bearing.
- radial and axial sliding surfaces are formed by a sliding bushing with a collar aligned in the radial direction, as a result of which the bearing arrangement in the radial direction can be realized as close as possible to the axis of rotation with a small space requirement.
- the primary part of the device for damping vibrations comprises at least two housing disks, which surround the secondary part to form an interior space.
- the bearing assembly is then arranged in the region of the axial extent of the arranged between the lock-up clutch and secondary housing housing disc between the latter and the output or the rotatably coupled thereto element.
- the second friction surface arrangement is then fastened in the radial direction outside of the bearing arrangement on the primary part.
- mounting plane and bearing arrangement are arranged in a plane which is writable by the axis of rotation and a perpendicular to this.
- This plane is arranged parallel to the planes of rotation of the individual elements of the device for damping vibrations.
- the turbine wheel of the hydrodynamic com- The second housing disc is either mounted only on a bearing arrangement with supporting action in the axial direction at the output or the rotatably connected with this element or free from storage relative to the output with the second hydrodynamic component facing housing disc of the primary part rotatably connected element out.
- the non-rotatably coupled to the output element is usually formed by an output hub. If the device for damping vibrations is designed with a closed housing, and the output hub sealingly guided with respect to the input, a passage opening in the hub is provided to guide the available resource flow in the power transmission device via the lock-up clutch.
- the solution according to the invention is suitable for power transmission devices with designs of the hydrodynamic component both as hydrodynamic speed / torque converter and hydrodynamic coupling. Furthermore, the device for damping vibrations can also be designed differently. Conceivable are pure Reibdämpfungs wornen or hydraulic damping devices. Primary and secondary are also referred to as primary and secondary masses and are generally designed as flywheels.
- Figure 1 illustrates in a schematic simplified representation of the inventive arrangement of the bearing assembly
- FIG. 2 illustrates, on the basis of an axial section through a power transmission device, a structural design according to FIG. 1;
- FIG. 3 illustrates a detail X according to FIG. 2.
- FIG. 1 shows, in a schematically simplified representation, the basic structure of a power transmission device 1 according to the invention with an inventive mounting of a device 2 for damping vibrations, in particular a torsional vibration damper.
- the power transmission device 1 comprises at least one input E and one output A, wherein the input E at least indirectly rotatably with a not dargestell- here Drive unit is connectable and the output A can be coupled with a not shown here and usually the power transmission device 1 downstream transmission module.
- the output A is therefore usually formed directly from a transmission input shaft 3.
- the power transmission device 1 further comprises a hydrodynamic component 4.
- This comprises at least one impeller P and a turbine wheel T, which is filled with a working fluid or working space AR for circulation and generation of a flow circuit, which is also referred to as a working cycle, between impeller P and turbine wheel T.
- the hydrodynamic component 4 is embodied as a hydrodynamic speed / torque converter 5, comprising in addition at least one stator wheel L.
- Embodiments not shown here as hydrodynamic clutches are also conceivable.
- the hydrodynamic component 4 is free of a stator.
- the hydrodynamic coupling transmits the torque while only the speed is variable.
- the hydrodynamic speed / torque converter 5 on the other hand serves both the speed / torque conversion as well. This usually stays filled.
- the impeller P is at least indirectly rotatably connected to the input E connectable, in the illustrated case directly rotatably connected thereto.
- the connection can be made detachable or insoluble.
- the coupling takes place via a co-rotating impeller shell 6.
- Designs with an impeller clutch as a separating clutch between impeller P and input E are also conceivable.
- the compound can also be designed in several parts.
- the turbine wheel T is at least indirectly non-rotatably connected to the output A of the power transmission device 1, that is, the transmission input shaft 3, connected.
- the coupling can take place directly via a so-called, here in the schematic representation only indicated output hub 7, which forms a rotatably connected to the output A element 8.
- connection can also take place via intermediate elements or units, for example, the device 2 for damping vibrations.
- the hydrodynamic component 4 the power purely hydrodynamic, that is wear-free between input E and output A, transmitted.
- the hydrodynamic component describes a hydrodynamic power branch. Since the efficiency is acceptable with respect to the connectable with the power transmission device 1 prime mover only in a certain operating range of these, the hydrodynamic component 4 is bridged.
- a device 9 for bypassing the hydrodynamic power branch is provided. This is designed as a lock-up clutch 10 and usually designed as a non-synchronous switchable coupling, that is, this is operated with slip.
- the lockup clutch 10 comprises a first friction surface arrangement 11 which is at least indirectly rotationally fixed means directly rotatably or indirectly via intermediate elements with the input E is connected and a second Reib lake extract 12 which is at least indirectly rotationally fixed to the output A, that is either coupled directly or via further transmission elements.
- the coupling with the output A from the side of the lock-up clutch 10 and also the hydrodynamic speed / torque converter 5 takes place in each case via the device 2 for damping vibrations.
- This comprises a first so-called primary part 13, which forms the input part of the device 2 and with the connecting elements, that is second friction surface 12 and further to the turbine wheel T rotatably connected and a secondary part 14, wherein the primary part 13 and secondary part 14 are arranged coaxially to each other and are limited rotatable relative to each other in the circumferential direction.
- Primary part 13 and Sekundärtei) 14 are coupled to each other via means 15 for transmitting torque and damping coupling.
- the device 2 acts as an elastic coupling, that is, a moment is transmitted, at the same time introduced via the primary part 13 vibrations are attenuated or reduced by the damping coupling.
- the means 15 for transmitting torque and damping coupling 15 can be formed by the same elements or different.
- the damping can be purely mechanical or hydraulic or a combination of both.
- corresponding spring units 16 are provided between the primary part 13 and the secondary part 14, which take over the function of torque transmission and storage of the vibration energy.
- the primary part 13 is formed, for example, by two housing disks 17 and 18, which surround the secondary part 14, which is designed, for example, in the form of a center disk 19, in the radial direction, axial direction and circumferential direction to form an interior space 20.
- connection to the lock-up clutch 10, in particular the output of the over-coupling 10 takes place, as already stated, rotationally fixed to the second friction surface arrangement 12, for example via fastening elements, in particular in the form of rivets.
- the bearing of the second friction surface arrangement 12 and the device 2 takes place at a common bearing point in the axial direction via a between the device 2 for damping vibrations and the second friction surface 12 of the lock-up clutch 10 arranged bearing assembly 22, at least either an axial or a radial support effect , preferably generates a supporting effect in both the axial and radial directions.
- the bearing assembly 22 is thus provided between the device 2 for damping vibrations and the output hub 7 and the output A of the power transmission device 1 and arranged in the axial direction in the region between the axial extent of lock-up clutch 10 and device 2.
- the bearing assembly 22 comprises in the simplest case two bearings - a thrust bearing 22 aX iai and a Ra warehouse 22 ra diai.
- a combined axial-radial bearing is provided.
- Another bearing arrangement 23 may be provided between the turbine wheel T and the device 2 for damping vibrations.
- this assumes only a maximum axial support in the axial direction opposite to the supporting force of the first bearing assembly 22. Therefore, it could also be dispensed with according to the specific structural design.
- the arrangement offers the advantage that the axial forces can be supported by the bridging clutch 10 in the direction of the device 2 for damping vibrations directly via the output hub 7 and / or its axial bearings. Furthermore, as a result of the force flow caused by this bearing arrangement 22, deformations and additional loads on the device 2 for damping vibrations are largely avoided.
- the radial bearing in the area of the lock-up clutch 10 allows for fewer tilting movements, which in turn lead to reduced and controlled friction and less tumbling.
- FIG. 1 illustrates only a schematically simplified representation of the basic arrangement and function of the individual bearings 22, 23, wherein the bearing arrangement 22 comprises both a radial and thrust bearing or these functions are taken over by a combined bearing.
- FIG. 2 illustrates a detailed embodiment on the basis of an axial section through a power transmission device 1, as it may be constructed in accordance with FIG.
- FIG. 3 shows the structure of the bearing arrangement 22 on the basis of the detail X according to FIG. 2.
- This bearing is preferably designed both as axial and radial bearings and designed in the form of a sliding bearing 24. According to the embodiment in Figure 2, the function of the sliding bearing 24 is taken over by a cranked sliding sleeve 25.
- the sleeve has in the radial direction to a projection 32 which extends in the circumferential direction in the manner of a collar and forms the radial and axial sliding surfaces.
- the primary part 13, in particular the housing plate 17, is in the radial direction to drawn in the region of the outer circumference 49 of the rotationally fixed to the output A coupled element 8 and has in its radially inner end portion 33 aligned in the axial direction trained collar 34, with its directed to the rotation axis R surface 35 and with the outer periphery 36 of the sliding sleeve 25 forms a press fit 37. It would also be conceivable that the sliding sleeve 25 is compressed with its inner circumference 26 on the element 8 connected to the output A in a rotationally fixed manner and forming the sliding pair between the outer circumference 36 of the sliding sleeve 25 and the inner circumference or collar on the primary part 13.
- the primary part 13, in particular the first, is supported by this Housing disc 17, on the non-rotatably coupled to the output A from element 8, free from a rotationally fixed coupling with this.
- the collar 34 is directed away in the case shown by the lock-up clutch 10 and directed to the hydrodynamic component 4 out.
- the power transmission device 1 is a combined unit of hydrodynamic speed / torque converter 5 and a lockup clutch 10, wherein the lockup clutch 10 is actuated by the pressure in the hydrodynamic component 4.
- a special actuator for example in the form of a piston, is not mandatory. In the simplest case, this can form a structural unit with the second friction surface arrangement 12.
- the actuating device 38 in the form of a piston member 39 rotatably with the turbine wheel T at least indirectly, that is coupled via further transmission elements, here the device 2 for damping vibrations.
- the second friction surface arrangement 12 comprises an inner disk carrier 40, which is non-rotatably connected to the housing, in particular the housing disk 17, on which the individual inner disks 41 are supported and also the actuating device 38 or the piston element 39.
- the illustrated unit, in particular the converter is designed as a two-channel system. This means that the hydrodynamic speed / torque wall 5 is essentially characterized by two connections, the latter being filled with operating means and the operating means remaining in the power transmission device 1 even when deactivated. This creates an external circuit that can also be used for cooling purposes. In converter operation, the power is transmitted hydrodynamically.
- the lock-up clutch 10 is open.
- the operating medium is circulated in the hydrodynamic component from the impeller P to the turbine wheel T and thereby transmits torque, converted by the blading of the guide wheel L.
- a type of external circuit is generated, in which operating Tel is discharged from the in the working space AR adjusting working circuit in the radial direction inward either externally cooled or via the lock-up clutch 10 via a gap 42 between actuator 38 and housing in the radial direction in the region of the outer circumference of the hydrodynamic component 4 in the gap between impeller P. and turbine wheel T is returned to the working space AR. If actuation of the lock-up clutch 10 is desired, the pressure in the working chamber AR is increased and the operating fluid flow in the external circuit is reversed.
- the operating medium emerges in the region of the outer circumference at the hydrodynamic component 4 in the gap between the primary wheel P and the turbine wheel T and acts on the actuating device 38, in particular the piston element 39, and leads to bringing the two friction surface arrangements 11 and 12 into engagement with one another.
- the lockup clutch 10 In particular, the two friction surface arrangements 11 and 12 extending in the radial directiondekanäie 43 extending in the radial direction from the region of the outer periphery to the inner periphery 45, a part is performed as a coolant via the lock-up clutch 10 and passes through the gap 42 again to the hydrodynamic speed
- a transverse bore 46 is provided according to the embodiment in Figure 2, which passes through the cooling oil flow of the lock-up clutch 10.
- the two connections to the hydrodynamic speed / torque converter 5 each serve to supply and / or drain operating resources.
- the device 2 for damping vibrations here has a closed primary part 13, that is, the two housing shells 17 and 18 form a housing, so that the available oil flow is always passed through the clutch and not by the device 2 for damping vibrations.
- Other versions are conceivable. This depends in detail on the specific embodiment of the device 2 for damping vibrations.
- a bearing assembly 22 with radial and / or axial support action for the primary part 13 of the device 2 for damping vibrations is critical, the arrangement considered in installation position between input E and output A or coupling with a power transmission device 1 downstream transmission unit within the the axial extension of the lock-up clutch 10 and the device 2 for damping vibrations takes place as a common bearing arrangement 22 for the second friction surface arrangement 12 and the device 2, in particular the primary part 13.
- the bearing arrangement 22 is furthermore preferably displaced in the radial direction into the radially inner region, that is, as close as possible to the axis of rotation R.
- the bearing 22 itself is designed at least either as a radial or thrust bearing or preferably as a combined radial and thrust bearing. This can be dispensed with further additional bearing arrangements and bearings.
- the bearing assembly 22 itself is formed in the simplest case as a sliding bearing. This is characterized in the radial and axial directions by small space.
- the embodiment according to FIG. 2 optionally illustrates a further sealing plate 47, which bears against the end lamella of the inner lamellae 41 and seals the inner lamella carrier 40 with respect to the end lamella and thus the individual inner lamellae 41.
- the turbine wheel T is preferably also non-rotatably connected to the primary part 13 via fastening elements 52.
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112007002249T DE112007002249A5 (en) | 2006-10-09 | 2007-09-13 | Power transmission device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006047639.5 | 2006-10-09 | ||
DE102006047639 | 2006-10-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008043331A1 true WO2008043331A1 (en) | 2008-04-17 |
Family
ID=38870262
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2007/001653 WO2008043331A1 (en) | 2006-10-09 | 2007-09-13 | Force transmission device |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112007002249A5 (en) |
WO (1) | WO2008043331A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014190986A1 (en) * | 2013-05-27 | 2014-12-04 | Schaeffler Technologies Gmbh & Co. Kg | Vibration-damped starter element for a drive train of a motor vehicle |
DE102009024744B4 (en) | 2008-06-26 | 2023-02-16 | Schaeffler Technologies AG & Co. KG | power transmission device |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19904857A1 (en) * | 1999-02-05 | 2000-08-10 | Mannesmann Sachs Ag | Hydrodynamic torque converter overcoming slip in its coupling permits mechanical assembly with free fluid flow and selective conversion, simplifying operation |
DE19926983A1 (en) * | 1999-06-14 | 2000-12-21 | Mannesmann Sachs Ag | Hydrodynamic torque converter has housing containing turbine wheel with casing and hub, torsional oscillation damper, cover discs and thrust piece |
JP2001116110A (en) * | 1999-10-19 | 2001-04-27 | Jatco Transtechnology Ltd | Torque converter with multiple disc lockup clutch |
US20010007383A1 (en) * | 2000-01-12 | 2001-07-12 | Mannesmann Sachs Ag | Torsional vibration damper |
FR2839128A1 (en) * | 2002-04-30 | 2003-10-31 | Valeo | Hydrokinetic coupling for motor vehicle transmission has axial rivets to form non-play connection between turbine wheel and hub, and damper |
DE10350935A1 (en) * | 2002-11-16 | 2004-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Method of improving oil flow through torque converter clutch friction plate prevents oil flow in specified zone of converter to increase flow over clutch friction plates |
FR2867540A1 (en) * | 2004-03-11 | 2005-09-16 | Luk Lamellen & Kupplungsbau | Motor vehicle torque converter with vibration damper has friction reducer between at least two components |
DE102004029157A1 (en) * | 2004-06-17 | 2005-12-29 | Zf Friedrichshafen Ag | Hydrodynamic torque converter has an axial load received by a covering metal sheet supported on an axially fixed component |
-
2007
- 2007-09-13 WO PCT/DE2007/001653 patent/WO2008043331A1/en active Application Filing
- 2007-09-13 DE DE112007002249T patent/DE112007002249A5/en not_active Withdrawn
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19904857A1 (en) * | 1999-02-05 | 2000-08-10 | Mannesmann Sachs Ag | Hydrodynamic torque converter overcoming slip in its coupling permits mechanical assembly with free fluid flow and selective conversion, simplifying operation |
DE19926983A1 (en) * | 1999-06-14 | 2000-12-21 | Mannesmann Sachs Ag | Hydrodynamic torque converter has housing containing turbine wheel with casing and hub, torsional oscillation damper, cover discs and thrust piece |
JP2001116110A (en) * | 1999-10-19 | 2001-04-27 | Jatco Transtechnology Ltd | Torque converter with multiple disc lockup clutch |
US20010007383A1 (en) * | 2000-01-12 | 2001-07-12 | Mannesmann Sachs Ag | Torsional vibration damper |
FR2839128A1 (en) * | 2002-04-30 | 2003-10-31 | Valeo | Hydrokinetic coupling for motor vehicle transmission has axial rivets to form non-play connection between turbine wheel and hub, and damper |
DE10350935A1 (en) * | 2002-11-16 | 2004-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Method of improving oil flow through torque converter clutch friction plate prevents oil flow in specified zone of converter to increase flow over clutch friction plates |
FR2867540A1 (en) * | 2004-03-11 | 2005-09-16 | Luk Lamellen & Kupplungsbau | Motor vehicle torque converter with vibration damper has friction reducer between at least two components |
DE102004029157A1 (en) * | 2004-06-17 | 2005-12-29 | Zf Friedrichshafen Ag | Hydrodynamic torque converter has an axial load received by a covering metal sheet supported on an axially fixed component |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009024744B4 (en) | 2008-06-26 | 2023-02-16 | Schaeffler Technologies AG & Co. KG | power transmission device |
WO2014190986A1 (en) * | 2013-05-27 | 2014-12-04 | Schaeffler Technologies Gmbh & Co. Kg | Vibration-damped starter element for a drive train of a motor vehicle |
CN105283694A (en) * | 2013-05-27 | 2016-01-27 | 舍弗勒技术股份两合公司 | Vibration-damped starter element for a drive train of a motor vehicle |
US9702447B2 (en) | 2013-05-27 | 2017-07-11 | Schaeffler Technologies AG & Co. KG | Vibration-damped starter element for a drivetrain of a motor vehicle |
DE112014002571B4 (en) | 2013-05-27 | 2023-02-16 | Schaeffler Technologies AG & Co. KG | Vibration-damped starting element for a drive train of a motor vehicle |
Also Published As
Publication number | Publication date |
---|---|
DE112007002249A5 (en) | 2009-06-25 |
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