WO2011054331A1 - Hydrodynamischer drehmomentwandler mit einem drehschwingungsdämpfer - Google Patents
Hydrodynamischer drehmomentwandler mit einem drehschwingungsdämpfer Download PDFInfo
- Publication number
- WO2011054331A1 WO2011054331A1 PCT/DE2010/001230 DE2010001230W WO2011054331A1 WO 2011054331 A1 WO2011054331 A1 WO 2011054331A1 DE 2010001230 W DE2010001230 W DE 2010001230W WO 2011054331 A1 WO2011054331 A1 WO 2011054331A1
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- WO
- WIPO (PCT)
- Prior art keywords
- centering
- thrust bearing
- axial
- disk
- torque converter
- Prior art date
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Classifications
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- 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
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- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
-
- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H2041/246—Details relating to one way clutch of the stator
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- 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
Definitions
- the invention relates to a hydrodynamic torque converter having a torsional vibration damper and an axial bearing arranged between a damper part of the torsional vibration damper or a turbine wheel of the hydrodynamic torque converter and an adjacent connection component and means for centering the axial bearing in the radial direction.
- Torque converter with a torsional vibration damper for example, from the publication DE 10 2006 028 771 A1 previously known.
- the turbine wheel of the hydrodynamic torque converter is attached to a damper input part of the torsional vibration damper and to a turbine hub.
- the damper output acting as damper output is connected to a damper hub and the damper hub in turn connected to a transmission input shaft of a downstream transmission.
- the attachment of the turbine wheel on the torsional vibration damper, in particular the damper input part and / or the turbine hub is effected by a Nietsch beidestatttell, including the turbine wheel and complementary to the damper input part fastening means, for example in the form of recesses are arranged.
- a thrust bearing is provided between the turbine hub and a connection component arranged in the axial direction, in particular a freewheel of a stator. If the turbine wheel and the damper input and the turbine hub are arranged for assembly, an alignment of all parts, including thrust bearings to each other is required so that the complementary recesses of turbine and damper input are superimposed, so that a rivet can be passed through both recesses.
- the thrust bearing is centered in the radial direction by a guide surface pointing in the radial direction on the turbine hub.
- a radial guide surface is provided on the turbine hub, which, in particular when designed as an aluminum die-cast part, makes the production correspondingly more complex.
- DE 10 2007 053 968 A1 discloses a torque transmission device free of a turbine hub, which has a hydrodynamic component in the form of a hydrodynamic speed / torque converter whose output in the form of the turbine wheel with a damper part of a downstream Torsional vibration damper, in particular a damper input is connected.
- the axial bearing between the damper input and the turbine wheel is realized here by a between the damper input and a freewheel side plate of the stator of the hydrodynamic component associated freewheel arranged thrust bearing.
- the invention has the object of providing a hydrodynamic torque converter with a torsional vibration damper of the type mentioned, in particular with a directly connected to the damper turbine wheel such that the mentioned disadvantages are avoided and the centering of the thrust bearing manufacturing technically simple and inexpensive while maintaining the axial and Radial support takes place.
- the solution according to the invention is carried out by the characterized by the features of claims 1, 8 and 10 embodiments, which can each be used alone or in combination with each other. Advantageous embodiments are described in the subclaims.
- a hydrodynamic torque converter having a torsional vibration damper and an axial bearing arranged between a damper part of the torsional vibration damper or a turbine wheel of the hydrodynamic torque converter and an adjoining connecting component and means for centering the axial bearing in the radial direction is characterized in that the directly supported via the thrust bearing Components are designed as disk-shaped components, wherein on at least one of the disk-shaped components, a centering means for centering the thrust bearing is formed.
- the damper-side disc-shaped component is formed in this and the other embodiments of the invention according to claims 8 and 10 of a damper part, in particular acting as a damper input side window.
- the Leitrad preparede component can be formed by a freewheel side window or other, supported on the stator component.
- the individual disc-shaped components of sheet metal components are formed, which can be manufactured in the simplest case with centering units as part of the centering means by separating and in a further embodiment by separating and forming.
- the only local training and arrangement of the centering also offers the advantage of being able to move the centering arbitrarily in areas of Axiallager environment, in particular to take advantage of available space effectively. Furthermore, there is also the possibility for to use the arrangement of the centering targeted areas between one of the disc-shaped components and the thrust bearing, which are limited in terms of the available free space in the circumferential direction.
- the solution according to the invention thus enables a total of particularly space-saving axial bearing arrangements with only slightly required modifications for centering.
- a plurality of centering means are provided, which are arranged offset from each other in the circumferential direction.
- the possibilities of arrangement are varied and can be distinguished with regard to the assignment to the individual disc-shaped components and the arrangement itself.
- the two or more centering means are each formed between the same disk-shaped component and the axial bearing. This possibility offers the advantage that the other disk-shaped component is particularly simple and inexpensive to produce, as this no modifications for centering are required. Furthermore, the positional assignment of the individual centering means to each other is clearly defined without further aids.
- the two or more centering means are each formed between different disc-shaped components and the thrust bearing. This solution is particularly important for specific space conditions of importance.
- the two or more centering means are preferably distributed uniformly in the circumferential direction in order to avoid imbalances.
- the arrangement can take place according to a first sub-education on a common or according to another sub-education on several arrangement diameters.
- a single centering means comprises a centering unit formed on the disk-shaped component and a centering unit designed to be complementary to the axial bearing, whereby a direct centering between disc-shaped component and thrust bearing is achieved and the associated tolerance chain is considerably shortened.
- the formation of the individual centering units can take place in a great variety of variants, which can be used individually or in combination with one another in a centering means or different centering means.
- the centering unit formed on the disk-shaped component comprises a radial guide surface extending over a partial region of the disk-shaped component in the circumferential direction and the centering unit formed on the axial bearing has a radial surface facing the guide surface on the axial bearing.
- the centering unit formed on the disk-shaped component comprises a guide surface facing the disk-shaped component in the circumferential direction and the centering unit formed on the axial bearing has a surface on the axial bearing pointing in the circumferential direction.
- the guide can be effected by form and / or adhesion between the guide surface on the disc-shaped member and the cooperating with this surface on the thrust bearing in the radial and / or circumferential direction.
- the individual centering units are designed such that a guide surface or surface is formed by an already existing surface area on the disk-shaped component or the axial bearing, in particular an axial bearing ring.
- a guide surface or surface is formed by an already existing surface area on the disk-shaped component or the axial bearing, in particular an axial bearing ring.
- no or only minor modifications are required on the other element, thrust bearing or disk-shaped component, whereby the production cost can be minimized and also find standardized elements for the disc-shaped member or the thrust bearing use.
- An example of such an embodiment consists in the formation of the individual guide surface on the disk-shaped component on an axial projection / projection and the training of this interacting surface of a thrust bearing already existing on the axial bearing ring surface or bearing housing surface.
- the centering unit formed on the disk-shaped component comprises a projection formed integrally therewith or formed in the form of a separately attached element and the centering unit formed on the axial bearing has a recess.
- the centering unit formed on the axial bearing is configured as a projection formed integrally or in the form of a separately attached element and the centering unit formed on the disk-shaped component as a recess.
- about these centering units can be done a tailor-made assignment, in particular by positive locking in both versions.
- the centering unit formed on the disk-shaped component or the thrust bearing can be formed by an axial material exhibition.
- an axial material exhibition is a local displacement of material from one side of the respective component, which occurs on the other side in the axial direction as an at least locally limited projection.
- the individual material exhibition is designed as a tab on the disk-shaped component.
- the formation of the tab is done by hinged folding out of material from the respective component.
- the tab shape is cut while maintaining a connection with the component in this and then pushed out.
- this can be carried out with respect to the connection axis with the component in such a way that the pushed-out regions are formed either by the separating surface formed during separation or by the pressed-out end face region of the disk-shaped component.
- Such tabs serve in particular the formation of radial guide surfaces.
- a further advantageous possibility is to carry out the individual material exhibition in the form of an enforcement. This is done by applying a pressure under plastic deformation at the opposite end face of the disc-shaped component or a radially extending portion of a thrust bearing or thrust bearing housing area causes. In this case, only material from a region in the axially formed projection is gathered together.
- the material displays in functional concentration form connecting or fastening elements, in particular form-locking connecting means.
- the individual centering means is formed in functional concentration as a rotationally fixed connection, which allows a fixed assignment of disc-shaped component and thrust bearing in all directions.
- connection or attachment means which in a first embodiment are integral with the individual disc-shaped component or the thrust bearing, in particular thrust bearing ring or bearing housing part are executed or are connected in a second embodiment as separate components with these.
- a particularly advantageous embodiment of this development serves the already existing connection between the damper part, in particular damper input part and turbine wheel, in particular turbine wheel the formation of the centering.
- the axial bearing between the damper part and Turbinenradrise is formed extended in the radial direction to the connection area, wherein the radial extent preferably along the front side of the disc-shaped member, in particular of the damper part takes place.
- no additional modifications to the disk-shaped components to be supported are required. This arrangement can therefore be retrofitted in existing configurations.
- a solution according to the invention according to a second embodiment of the hydrodynamic torque converter with a torsional vibration damper and between a damper part of the torsional vibration damper or connected to this turbine of the hydrodynamic torque converter and an adjacent connection member arranged thrust bearing and means for centering the thrust bearing in the radial direction, characterized in that the directly supported via the thrust bearing components are designed as disc-shaped components, wherein at least one of the disc-shaped components and the thrust bearing are designed such mount the thrust bearing on the disc-shaped member or a gap between this and a connecting element, in particular a hub.
- the suspension is preferably carried out on radial guide surfaces on the disk-shaped component by the interaction with radial surfaces on the thrust bearing.
- the radial guide surfaces may be formed as circumferential guide surfaces or extending in the circumferential direction extending guide surface segments. By analogy, this also applies to the individual surfaces on the thrust bearing.
- the thrust bearing can by training a corresponding radial extension to the diameter of the inner circumference of the damper part and a corresponding axial elevation to form radial guide surfaces on the inner circumference of the damper part are attached to this.
- a second variant is the formation of centering units in the form of axial
- Elevations on the thrust bearing characterized in the axial direction in centering units in the form of recesses on the disc-shaped component can be suspended.
- the centering unit formed on the disk-shaped component thus forms a radial guide surface extending over a partial region of the disk-shaped component in the circumferential direction and the centering unit formed on the axial bearing has a radial surface facing the axial bearing.
- the centering unit embodied on the disk-shaped component comprises a guide surface facing the disk-shaped component in the circumferential direction and rotating in the circumferential direction and the centering unit formed on the axial bearing has a surface on the axial bearing pointing in the circumferential direction.
- the guide can be effected by positive and / or frictional engagement between the guide surface on the disk-shaped component and the surface cooperating with this in the radial and / or circumferential direction.
- a third variant of the second embodiment according to the invention is characterized in that the suspension takes place at a level of offset provided on the disc-shaped component. This is ensured by appropriate shaping of the disk-shaped component to form a radial guide surface formed in the radial extension region and the complementary design of the subsequent axial bearing ring to form radial surfaces which cooperate with the guide surfaces on the disk-shaped component.
- the centering can take place on a hub, a component rotatably connected to the disk-shaped component, in particular the turbine wheel or the turbine wheel disk. Furthermore, the centering can be done via a simple additional, radial guide surfaces forming centering. In this case, it is possible to perform the individual components involved in the axial bearing, in particular the thrust bearing itself and the disc-shaped components particularly simple and compact and only adapt the centering function by additional elements to the specific structural conditions.
- damper part in particular damper input part and / or a rotatably connected thereto component and a paddle wheel of a hydrodynamic component or a non-rotatably coupled thereto element suitable.
- the arrangement between the damper part, in particular damper input and stator according to a further variant between the turbine wheel and a stator of a hydrodynamic component.
- the solution according to the invention is particularly suitable for centering the thrust bearing on a damper part which is not supported directly on a hub.
- FIG. 3 shows a further variant of a first embodiment according to the invention of the means for centering on the basis of a section of an axial section of a
- FIG. 4 shows a further variant of a first embodiment according to the invention of the means for centering on the basis of a section of an axial section of a
- FIG. 6a shows a further variant of a first embodiment according to the invention of the means for centering on the basis of a section of an axial section of a torque transmission device
- Figures 6b and 6c show possible embodiments of the variant according to Figure 6a in one
- FIG. 8 shows a further variant of a first embodiment according to the invention
- FIG. 11 shows a first variant of a third embodiment of the centering device according to the invention on the basis of a detail of an axial section of a torque transmission device
- FIG. 12 shows a further variant of a third embodiment according to the invention of the means for centering on the basis of a section of an axial section of a torque transmission device
- FIG. 13 shows a further variant of a third embodiment according to the invention of the means for centering on the basis of a detail of an axial section of a torque transmission device
- FIG. 1 illustrates, in a schematized and greatly simplified illustration, the example of a torque transmission device 1, of the arrangement and construction of an inventively designed centering of an axial bearing 2 on a damper input part.
- the torque transmission device 1 comprises at least one input E and at least one output A, which is rotatably connected, for example, with a transmission input shaft of a downstream transmission unit.
- the input E is at least indirectly with a drive unit, not shown here, that is connected directly or via further transmission elements.
- the torque transmission device 1 comprises at least one hydrodynamic component and a device for damping vibrations, also referred to below as torsional vibration dampers 4 for short.
- the hydrodynamic component can be designed in various ways.
- the hydrodynamic torque converter 3 is arranged in the power flow between the input E and the output A. This is downstream of the torsional vibration damper 4 in the power flow in the illustrated embodiment.
- the hydrodynamic torque converter 3 comprises at least one at least indirectly rotatably connected to the input E of the torque transmitting device 1 and viewed in the direction of power flow from the input E to the output A considered impeller P acting paddle wheel and at least indirectly connected to the output A turbine T. Pump impeller P and turbine wheel T form a working space that can be filled with operating fluid.
- at least one stator L is additionally provided as a reaction member.
- the hydrodynamic torque converter serves for the simultaneous conversion of speed and torque.
- the hydrodynamic torque converter 3 is followed by the torsional vibration damper 4 in the power flow.
- the turbine T with the torsional vibration damper 4 is rotatably connected.
- the torsional vibration damper 4 comprises at least one single or multi-part first damper part, which is also referred to as damper input part, and another, one or more parts second damper part, which is at least indirectly connected to the output A rotatably.
- Both damper parts 4.1 and 4.2 are arranged coaxially with each other and limited relative to each other in the circumferential direction rotatable limited.
- damper parts 4.1 and 4.2 can be done directly via means 5 for torque transmission and / or means 6 for damping coupling, which are preferably formed with the same functional components in the form of spring units Fn, which are designed as single springs or spring packs and with the Support end sections alternately on damper parts 4.1 and 4.2.
- spring units Fn which are designed as single springs or spring packs and with the Support end sections alternately on damper parts 4.1 and 4.2.
- the torsional vibration damper 4 it is possible to form the torsional vibration damper 4 as a multi-stage damper assembly.
- the damper part 4.1 and the damper part 4.2 are coupled together in this case via at least two damper stages, which may be connected in series and / or in parallel.
- damper part 4.1 takes place on an axial connection component 7.
- axial connection component 7 In this example may be the stator L or between the stator L and the respective support for this intended freewheel F act. It is necessary to center the thrust bearing 2 in its position in the radial direction relative to the torsional vibration damper 4 and the hydrodynamic torque converter 3.
- the components supported directly via the axial bearing 2 are designed as disc-shaped components S1, S2, and means 10 for centering the axial bearing 2 are provided.
- centering means 11 can be designed as centering means 11, suspension 34 or separate centering elements 43, as described below.
- the centering serves the radial guidance of the axial bearing 2 with respect to the connection components.
- the thrust bearing 2 itself can be designed in various ways. This can be a rolling or sliding bearing. Decisive is the arrangement between two spaced apart in the axial direction with respect to the axis of rotation R arranged disc-shaped components S1, S2 to each other in the axial direction facing connecting surfaces.
- Damper part 4.1 which here consists of two axially spaced side windows 8 and 9, to the side window 9.
- connection of the turbine wheel T can be made directly to the side window 9.
- the axial forces acting on these are supported via the axial bearing 2 on a connection component, here for example on the stator L or a component of the freewheel F.
- the torque transmission device further comprises by way of example a shiftable clutch device 12, comprising a first clutch part 12. 1, which is at least indirectly connected in a rotationally fixed manner to the input E, and a second clutch part 12. 2, which is connected to the torsional vibration damper 4.
- the switchable coupling device 12 serves here for the at least partial bypassing of the force flow via the hydrodynamic component 3.
- the shiftable clutch is used for the complete bridging of the hydrodynamic torque converter 3.
- the switchable coupling 12 is designed in disc design, preferably in lamellar construction.
- each coupling part 12.1 and 12.2 a plate carrier 13 and 14, on which non-rotatably reib laketragende and / or frictional surface-forming elements are arranged displaceably in the axial direction, which are engageable with each other via an actuating device 17 in operative connection.
- the non-rotatable connection between the coupling part 12.1 and the input E can take place via corresponding connecting elements or else an integral embodiment of the input E with the plate carrier 13.
- the disk carrier 14, which is exemplified here as an inner disk carrier is rotatably connected to the torsional vibration damper 4, here the side plate 8 of the damper part 4.1.
- the thrust bearing 2 is guided on two disk-shaped components S1 and S2, being provided on at least one disc-shaped component S1 means for radial guidance.
- This disk-shaped component S1 is formed in a particularly advantageous embodiment directly from the damper part 4.1, in particular the side window 9.
- the following figures illustrate particularly advantageous embodiments inventively executed Axiallagerzentrierept for fixing the position of the axial bearing 2 between two disc-shaped components S1 and S2 in the form of a side window 9 of the damper part 4.1 and an axial ring 18 in the form of a freewheel disk on the freewheel F of the stator L based on a section of the Storage environment of the thrust bearing 2 in a torque transmission device 1.
- the side plate 9 is designed as a disk-shaped component S1 and the axial ring 18 as a disk-shaped component S2.
- Other embodiments of the connection component 7, in particular of the disk-shaped component S2 are conceivable. In this case, all subsequent figures represent the same installation situation, which is why the same reference numerals are used for the same elements.
- the axial support takes place on a contact surface 24, which is formed on the side facing the hydrodynamic torque converter 3 end face 23.2 pointing in the axial direction.
- a turbine 25 which is either rotatably connected to the turbine T or forms an integral unit.
- the rotationally fixed connection is denoted by 26.
- the thrust bearing 2 is here arranged directly between the damper part 4.1 and an axial ring 18 supported on an outer ring 19 of a freewheel F. The arrangement is effected between two disk-shaped components S1 and S2, the first disk-shaped component S1 being formed by the damper part 4.1, in particular the side disk 9, and the second disk-shaped component S2 by the axial ring 18.
- the axial bearing 2 comprises by way of example a thrust bearing ring AR1 which is supported in the axial direction on the disk-shaped component S1, in particular the side disk 9, and an axial bearing ring AR2 which is supported on the axial ring 18. Between these rolling elements ARW are provided.
- FIGS. 2 to 5 illustrate, on the basis of a resulting storage situation, the arrangement of the axial gers 2 between the damper input forming damper part 4.1 of the torsional vibration damper 4, in particular the side plate 9 and a connection member provided in the axial direction 7, the formation of the centering means 10 according to a first embodiment of the invention.
- At least one of the disk-shaped components S1 or S2, in this case S1 and the axial bearing 2 are designed in this first embodiment to form centering means 11 locally at at least one point within the radial extension region of the disk-shaped component S1.
- the individual centering means 11 comprise a centering unit 11.1 formed on a disk-shaped component and a centering unit complementary thereto on the axial bearing 2, which can be brought into operative connection with one another.
- the centering units 11.1 on the disk-shaped components S1 are formed by axial material displays 20 extending over a partial area in the circumferential direction.
- the individual centering unit 11.1 in the form of material exhibits 20 in Figures 2 to 4, a radial, extending over partial area in the circumferential direction guide surface 27 for the thrust bearing 2, in particular for guiding a radial surface 28 on the thrust bearing 2.
- In the circumferential direction are preferably spaced at least two such centering means 11 or other centering provided.
- the individual material exhibition 20 is designed as a tab 29 on the disk-shaped component S1.
- the tab 29 is arranged and formed such that it forms a radially outwardly facing guide surface 27.
- the tab 29 is arranged radially inside the axial bearing 2, in particular its inner circumference.
- such tabs 29 are material protrusions cut out of the material of the disk-shaped element S1 and produced by deformation in the axial direction. These are executed on the axial bearing facing end face 9.2 of the side window 9.
- FIG. 2 illustrates an embodiment in which the tab 29 is formed by a material display at right angles to the end face 9. 2 of the side window 9.
- the radial guide surface 27 of the tab 29 is formed here by the pressed-out from the end face 9.1 portion.
- Figure 3 illustrates an alternative embodiment of the individual
- the guide surface 27 is determined by the by the separation of the La formed form of the surrounding material on the tab formed separating surface.
- the bearing on the guide surface 27 surface 28 on the thrust bearing 2 is formed in both cases by way of example of an already existing surface on the axial bearing ring AR1 or a bearing housing.
- Figure 4 shows an advantageous development in integral design by forming axial projections or elevations
- the shaping takes place by expressing material, for example in the form of cylindrical pins or other geometries in the axial direction of the component.
- the centering unit 11.1 here comprises the individual material exhibits 20, which form the radial guide surface for the, the centering unit 11.2 forming surface 28 of the thrust bearing 2 with partial areas of their outer peripheral surfaces.
- the axial bearing ring AR1 is designed to be extended in the radial direction, in this case into the radial region within the inner circumference of the axial bearing 2, wherein the recess 32 formed as a passage opening is arranged in the region of this extension.
- the extension and thus arrangement of the individual centering means 11 can also take place in the radial direction in a region outside of the axial bearing 2.
- the interlocking elements 31 may be formed in many forms. In a particularly advantageous embodiment, these form aligned in the axial direction pins or segments. Any cross-sectional geometry of the axial material exhibits 20 is conceivable.
- All embodiments shown in FIGS. 2 to 5 preferably require at least two such material displays 20 arranged at a distance from one another in the circumferential direction to ensure a sufficient centering effect.
- these are arranged in the circumferential direction on a common arrangement diameter and opposite each other.
- FIG. 6a shows a possible alternative to FIG. 5 with the embodiment of the centering unit 11.1 on the disk-shaped component S1 in the form of a recess 37, in particular through opening and the centering unit 11.2 on the axial bearing 2 in the form of an axial projection 38.
- This is supported on the disk-shaped component S1
- Axiallagerring AR1 is formed and engages in the recess 37, whereby a suspension of the Axiallagerringes AR1 takes place on the disk-shaped member S1.
- FIGS. 6b and 6c illustrate, for example, different possibilities of centering.
- FIG. 6b illustrates, for an embodiment according to FIG. 6a, in a view A on the side window 9, the centering unit 11.1 with the recess 37, in which the axial elevation 38 of the centering unit 11.2 is rendered engaging.
- the recess 37 forms radial guide surfaces 27, the axial projection 38 forms radial surfaces 28 on the thrust bearing 2, in particular thrust bearing ring AR1.
- Figure 6c illustrates an embodiment with flankenzentriertem engagement of the axial elevation 38 in the recess 37. It is formed in the recess 37 of the centering 11.1 guide surfaces 35 with the circumferentially oriented surfaces 36 of the centering unit 11.2 in the form of the axial elevations 38 in the circumferential direction achieved a positive connection or adhesion. Also for this embodiment, the aforementioned statements regarding the arrangement and selected number of individual centering 11 apply.
- FIGS. 7 and 8 show further variants of the design of the centering means 11 according to the first embodiment of the invention. These simultaneously form non-rotatable connections 39 between a disk-shaped component, here S1 and the axial bearing 2, in particular the axial bearing ring AR1.
- the axial elevations on one of the components, disc-shaped component S1 or thrust bearing 2 can be formed by integral or separate fastening elements which form the connection 39 with the centering unit on the other component.
- FIG. 7 shows a design of the centering units 11.1 and 11.2 with the formation of a connection 39, in particular a non-detachable connection by riveting with integral formation of the fastening elements on the disk-shaped component S1 in the form of the axial material display 20.
- FIG. 7 shows a particularly advantageous embodiment with high functional concentration.
- All of the aforementioned variants of centering means 11 formed according to the invention can also be provided on the axial ring 18. Furthermore, all the aforementioned embodiments can also be provided and arranged outside the axial bearing 2 in the radial direction.
- FIG. 8 shows an advantageous embodiment of the centering means 11 with the formation of a connection 39, in which case connections existing in any case in the storage environment are used.
- the centering unit 11.1 on the disk-shaped component S1 comprises a recess 37 designed as a passage opening and fixing or connecting elements 33 connected thereto in the form of rivet bolts, which are guided through recesses 32 on the axial bearing 2, in particular axial bearing ring AR1.
- the axial bearing ring AR1 is arranged between the disk-shaped component S1 and the turbine wheel T or a member, in particular the turbine wheel disk 25, connected to it in a rotationally fixed manner and fastened to these components.
- the centering takes place directly in the connection point between the torsional vibration damper 4 and the turbine wheel T.
- Figures 9 to 11 show possible variants of the centering according to a second embodiment of the invention by hooking.
- the means 10 comprise means 34 for mounting the thrust bearing 2 in at least one of the adjacent disk-shaped components S1 and / or S2. These comprise at least circumferentially circumferentially running or a plurality of circumferentially spaced radial guide surfaces 27 on one of the disk-shaped components S1 or S2 and cooperating with these complementary radial surfaces 28 or a circumferential surface 28 on the thrust bearing 2.
- the thrust bearing 2 in axial Direction extending survey, in particular a projection 38 is provided which forms the facing in the radial direction surface or surfaces 28.
- the figure 9 shows a first particularly advantageous variant which does not require any modification to the disk-shaped component S1.
- the axial bearing ring AR1 is shaped such that it is designed to extend in the radial direction in the direction of the inner circumference of the disk-shaped component S1, the axial projection 38 being made engaging in the intermediate space 41 formed between the damper hub 23 and the inner circumference of the damper part 4.1.
- the axial bearing ring AR1 has for this purpose an axial or a plurality of axial projections 38, which form a radially-facing surface 28, which cooperate with the inner circumference of the side plate 9 and the radial guide surface 27 formed by this.
- the axial projection 38 may be annularly closed in the circumferential direction to form a circumferential surface 28 in the circumferential direction.
- the entire thrust bearing ring AR1 is Z-shaped when viewed in cross-section. It is also conceivable here to provide only individual axial projections 38 in the circumferential direction, which are arranged at a distance from one another.
- the disk-shaped component S1 here forms an axially deformed region which forms a guide surface 27 pointing in the radial direction to the axis of rotation R, which can be brought into operative connection with a complementary guide surface 28 on the axial bearing ring AR1 and effects centering.
- the suspension can be closed or segmented in the circumferential direction, that is to say the two guide surfaces 27 and surfaces 28 which can be brought into operative connection are designed to be circumferential or at least one of these surfaces is designed as circumferentially circumferentially closed surface or if a plurality of partial surfaces are used. which are spaced from each other, formed.
- FIGS. 11 to 13 show variants of a third embodiment of the solution according to the invention by centering on one of the connection components.
- the means 10 in Figure 1 comprise a centering in the radial direction in the region of the outer circumference of the axial bearing 2 or outside by extension of one of the Axiallagerringe, here the Axiallagerringes AR1 in the radial direction in the area outside of the thrust bearing 2.
- the centering takes place in Figure 11 the turbine wheel 25 or a non-rotatably connected thereto element, in particular formed on these tabs 42 in the radial direction.
- FIG. 13 illustrates a further third variant of the third embodiment with an additional centering element 43, while for the previously mentioned variants, the centering arrangements have been formed integrally on one of the components.
- the additional centering element 43 is designed here in the form of a centering plate. This is so fitted between thrust bearing 2 and a connection element, here the gap 41 between the damper part 4.1 and damper hub 23, that a radial guidance takes place.
- the centering element 43 is pressed radially inward on the axial bearing ring AR1 or a connection element on the latter, and also alternatively within the intermediate space between disk-shaped component S1 and damper hub 23. Alternatively, this can also be positively connected to one of the components.
- the centering element 43 forms radial surfaces 44.1 for support on guide surfaces 27 on the side window 9, which is formed by a surface formed on the inner circumference. Furthermore, the centering element 43 forms radial surfaces 44.2 for interacting with radial surfaces 28 on the axial bearing 2.
- friction surface carrying and / or frictional surface forming elements friction surface and / or friction surface forming elements actuating device
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010004331.0T DE112010004331B4 (de) | 2009-11-09 | 2010-10-18 | Hydrodynamischer Drehmomentwandler mit einem Drehschwingungsdämpfer |
US13/460,937 US8813483B2 (en) | 2009-11-09 | 2012-05-01 | Hydrodynamic torque converter with torsion vibration damper |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009052295 | 2009-11-09 | ||
DE102009052295.6 | 2009-11-09 | ||
DE102010027255.8 | 2010-07-15 | ||
DE102010027255 | 2010-07-15 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/460,937 Continuation US8813483B2 (en) | 2009-11-09 | 2012-05-01 | Hydrodynamic torque converter with torsion vibration damper |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011054331A1 true WO2011054331A1 (de) | 2011-05-12 |
Family
ID=43530261
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/001230 WO2011054331A1 (de) | 2009-11-09 | 2010-10-18 | Hydrodynamischer drehmomentwandler mit einem drehschwingungsdämpfer |
Country Status (3)
Country | Link |
---|---|
US (1) | US8813483B2 (de) |
DE (2) | DE112010004331B4 (de) |
WO (1) | WO2011054331A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITTO20120256A1 (it) * | 2012-03-21 | 2013-09-22 | Dayco Europe Srl | Gruppo convertitore di coppia per un veicolo |
US20150369069A1 (en) * | 2014-06-24 | 2015-12-24 | Schaeffler Technologies AG & Co. KG | Stator body centering feature for torque converter |
US9494220B2 (en) * | 2014-10-21 | 2016-11-15 | Caterpillar Inc. | Apparatus for controlling operation of a torque converter |
US10344843B2 (en) * | 2016-11-04 | 2019-07-09 | Schaeffler Technologies AG & Co. KG | Torque converter bushing for aligning bearing between turbine and stator |
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US4733979A (en) * | 1985-12-04 | 1988-03-29 | Ntn Toyo Bearing Co., Ltd. | Thrust roller bearing assembly |
DE4330264A1 (de) * | 1992-09-07 | 1994-03-10 | Daikin Mfg Co Ltd | Verriegelungsvorrichtung für einen Drehmomentwandler |
DE19852772A1 (de) * | 1997-11-18 | 1999-06-02 | Jatco Corp | Drehmomentwandler für ein Fahrzeug |
WO2002001091A1 (fr) * | 2000-06-29 | 2002-01-03 | Valeo | Appareil d'accouplement hydrocinétique, notamment pour véhicule automobile, comportant une butée à aiguilles entre le piston et le moyeu de turbine |
DE102005006253A1 (de) | 2005-02-11 | 2006-08-17 | Daimlerchrysler Ag | Verfahren zum unlösbaren Befestigen |
DE102006028771A1 (de) | 2006-06-23 | 2008-01-03 | Daimlerchrysler Ag | Hydrodynamischer Drehmomentwandler und Verfahren zur Herstellung eines solchen |
DE102007053968A1 (de) | 2006-11-29 | 2008-06-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentübertragungseinrichtung |
US20080185257A1 (en) * | 2006-09-06 | 2008-08-07 | Toyota Jidosha Kabushiki Kaisha | Stator support structure for a torque converter |
DE102009007061A1 (de) * | 2008-02-19 | 2009-08-20 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentwandler mit Zentrierung und Halterung des turbinenseitigen Lagers am Leitrad |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4073666B2 (ja) * | 2001-12-27 | 2008-04-09 | 株式会社エクセディ | ロックアップ装置付き流体式トルク伝達装置 |
-
2010
- 2010-10-18 WO PCT/DE2010/001230 patent/WO2011054331A1/de active Application Filing
- 2010-10-18 DE DE112010004331.0T patent/DE112010004331B4/de active Active
- 2010-10-19 DE DE102010048874A patent/DE102010048874A1/de not_active Withdrawn
-
2012
- 2012-05-01 US US13/460,937 patent/US8813483B2/en not_active Expired - Fee Related
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4733979A (en) * | 1985-12-04 | 1988-03-29 | Ntn Toyo Bearing Co., Ltd. | Thrust roller bearing assembly |
DE4330264A1 (de) * | 1992-09-07 | 1994-03-10 | Daikin Mfg Co Ltd | Verriegelungsvorrichtung für einen Drehmomentwandler |
DE19852772A1 (de) * | 1997-11-18 | 1999-06-02 | Jatco Corp | Drehmomentwandler für ein Fahrzeug |
WO2002001091A1 (fr) * | 2000-06-29 | 2002-01-03 | Valeo | Appareil d'accouplement hydrocinétique, notamment pour véhicule automobile, comportant une butée à aiguilles entre le piston et le moyeu de turbine |
DE102005006253A1 (de) | 2005-02-11 | 2006-08-17 | Daimlerchrysler Ag | Verfahren zum unlösbaren Befestigen |
DE102006028771A1 (de) | 2006-06-23 | 2008-01-03 | Daimlerchrysler Ag | Hydrodynamischer Drehmomentwandler und Verfahren zur Herstellung eines solchen |
US20080185257A1 (en) * | 2006-09-06 | 2008-08-07 | Toyota Jidosha Kabushiki Kaisha | Stator support structure for a torque converter |
DE102007053968A1 (de) | 2006-11-29 | 2008-06-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentübertragungseinrichtung |
DE102009007061A1 (de) * | 2008-02-19 | 2009-08-20 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentwandler mit Zentrierung und Halterung des turbinenseitigen Lagers am Leitrad |
Also Published As
Publication number | Publication date |
---|---|
US8813483B2 (en) | 2014-08-26 |
US20120210707A1 (en) | 2012-08-23 |
DE112010004331B4 (de) | 2022-08-18 |
DE102010048874A1 (de) | 2011-05-26 |
DE112010004331A5 (de) | 2012-08-16 |
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