EP3025070A1 - Drehschwingungsdämpfungsanordnung für den antriebsstrang eines kraftfahrzeugs - Google Patents
Drehschwingungsdämpfungsanordnung für den antriebsstrang eines kraftfahrzeugsInfo
- Publication number
- EP3025070A1 EP3025070A1 EP14731662.4A EP14731662A EP3025070A1 EP 3025070 A1 EP3025070 A1 EP 3025070A1 EP 14731662 A EP14731662 A EP 14731662A EP 3025070 A1 EP3025070 A1 EP 3025070A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- vibration damping
- torsional vibration
- damping arrangement
- rotation
- arrangement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/1204—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system
- F16F15/1206—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system with a planetary gear system
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/13157—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses with a kinematic mechanism or gear system, e.g. planetary
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
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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
- F16H2045/0221—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
- F16H2045/0268—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 the damper comprising a gearing
Definitions
- Embodiments of the present invention relate to a torsional vibration damping arrangement for the drive train of a vehicle having an input region to be driven for rotation about a first rotation axis, an output region, a first torque transmission path extending from the input region to the output region, a second torque transmission path extending from the input region to the output region, and a coupling arrangement connected to the output area for superimposing torques conducted via the torque transmission paths, wherein the coupling arrangement comprises a planetary gear with a planetary gear, which is rotatable about a second axis of rotation.
- a torsional vibration damping arrangement which divides a in an input area, for example by a crankshaft of a Annebsaggregats, initiated torque in a guided over a first Wheelmomentübertragungsweg torque component and a guided over a second Drehmomentübertragungsweg torque component.
- this torque distribution not only a static torque is divided.
- a coupling or overlay arrangement which may be embodied as a planetary gear with a planet carrier
- the torque components transmitted via the two torque transmission paths are brought together again and then introduced as a total torque into an output region, for example a friction clutch, a transmission or the like.
- a phase shifter arrangement with an input element and an output element is provided, which is constructed in the manner of a vibration damper, ie with a primary side and a rotatable by a compressibility of a spring arrangement with respect to this Secondary side.
- a vibration damper ie with a primary side and a rotatable by a compressibility of a spring arrangement with respect to this Secondary side.
- the vibration components routed via the other torque transmission path experience no or possibly a different phase shift
- the vibration components contained in the torque components combined by means of the coupling arrangement and mutually phase-shifted can be destructively superimposed on one another, so that in the ideal case the total torque introduced into the output region essentially follows is no vibration component static torque contained.
- FIG. 1 schematically shows a torsional vibration damping arrangement 10, which operates on the principle of power branching or torque branching.
- the torsional vibration damping arrangement 10 may be in a drive train of a vehicle between a drive unit 12 and a subsequent part of the drive train, so for example a starting element 14, such.
- a friction clutch As a friction clutch, a hydrodynamic torque converter or the like can be arranged.
- the torsional vibration damping assembly 10 includes an input portion, generally designated 16. In the input region 1 6, a torque absorbed by the drive unit 12 branches into a first torque transmission path 18-1 and a second torque transmission path 18-2.
- first coupling arrangement input part 22 which, for example, comprises a planet or ring gear carrier 24 can and a second coupling arrangement input part 26, which may have a drive sun gear 28, introduced into the coupling assembly 20 and merged there again.
- first coupling arrangement input part 22 which, for example, comprises a planet or ring gear carrier 24
- second coupling arrangement input part 26 which may have a drive sun gear 28, introduced into the coupling assembly 20 and merged there again.
- the coupling arrangement 20 may be embodied, for example, as a planetary gear 30.
- a first planetary gear 32 and a second planetary gear 34 can be mounted radially successively and axially overlapping or overlapping rotatably.
- the first planetary gear 32 can intermesh on the one hand with the drive sun gear 28 and on the other hand with the second Pianetenrad 34.
- the second planetary gear 34 serves to reverse the direction of rotation. From the second planet gear 34, the converged torque via an output member 36 which may include, for example, a Abriosshohlrad 38, which also meshes with the second planet gear 34 and is rotatably connected to an output portion 40, to the starting element 14, such as a clutch or a Geared.
- a vibration system indicated generally by the reference numeral 42 is integrated.
- the vibration system 42 is operative as a phase shifting arrangement and includes a primary mass 44 to be connected to the prime mover 12, an input member 46 non-rotatably connected to the primary mass 44, and a spring assembly 48 connected to the input member 46.
- An output member 50 of the spring assembly 48 is further provided with a Intermediate element 52 is connected, which forms here by way of example the planet carrier 24 and on which the first planetary gear 32 and the second planetary gear 34 is rotatably mounted.
- the planet carrier 24 is positioned, for example, in the first torque transmission path 18-1, which has a phase shift from the rotational nonuniformities directed via the first torque transmission path 18-1 with respect to the rotational nonuniformities conducted via the second torque transmission path 18-2.
- the output member 50 of the spring assembly 48 is rotatably coupled to the Planentenradveti 24, form the phase shifter assembly 42 and the coupling assembly 20 a, in axial extent, compact unit.
- Another positive for a decoupling is that inertia of the Planetenradt- carrier 24 and the first and second planetary gear 32, 34 enter into the inertia of the intermediate element 52.
- a torque curve in the first torque transmission path 18 - 1 can come from the drive unit 12 via the primary mass 44 and the input element 46 extend into the spring assembly 48.
- the first torque via the output member 50 of the spring assembly 48 and the intermediate member 52 to the Planetenradtrager 24, which receives the first planetary gear 32 and the second Pianetenrad 34 primarily.
- the output element 50, the intermediate element 52 and the Pianetenradarme 24 rotatably coupled to each other.
- the second torque is transmitted from the drive unit 12 to a drive sun gear 28 rotatably connected thereto.
- the drive sun gear 28 meshes with the first planetary gear 32 and thereby guides the second torque to the first planetary gear 32 of the coupling assembly 20.
- the second planetary gear 34 which meshes with the first planetary gear 32, serves to reverse the direction of rotation, before the converged torque is guided by the second planetary gear 34 via the output ring gear 38 to the output region 40, to which the starting element 14, for example a friction clutch, a transmission or a torque converter is attached, which are not shown here.
- an additional mass element 54 can be fastened in a rotationally fixed manner to the intermediate element 52.
- An additional improvement of the decoupling can be achieved by the positioning of a known mass pendulum 56 on the intermediate element 52.
- Such torsional vibration damping assemblies 10 may, in addition to hydrodynamic torque converters between a converter lock-up clutch and a
- Output unit such as. B. a transmission input shaft can be switched.
- converter lock-up clutch, torsional vibration damping arrangement and hydrodynamic torque converter in a common housing, for. B. within a bell housing are.
- FIG. 2a shows a torsional vibration damping arrangement 10 'according to a similar principle as described in FIG. 1, as an application in conjunction with a hydrodynamic torque converter 90 as a starting element.
- the resulting starting element comprises predominantly the torque converter 90 with a converter lock-up clutch 62 and the torsional vibration damping arrangement 10 ', which is arranged between the converter lock-up coupling 62 and a power take-off unit, such as a power take-off.
- B. is arranged a transmission input shaft.
- the torsional vibration damping arrangement 10 ' comprises, as already described with reference to FIG. 1, a first and a second torque transmission path 18-1 and 18-2, a phase shift arrangement 42 and a coupling arrangement 20 in the form of a planetary gear.
- Figure 2b shows a torque curve with closed converter lerüber Wegkupplung 62
- the figure 2c shows a torque curve when the converter lock-up clutch 62 is open.
- Figures 2b and 2c can be seen with reference to the descriptions of Figure 2a.
- a total torque Mg which may come from a drive unit 12, for example an internal combustion engine, passes via a crankshaft 19 to a converter housing 95. Further, the total torque Mg is guided from the converter housing 95 via a converter clutch drive 63 into the converter lock-up clutch 62. As a result of a torque converter lock-up clutch 62 closed in accordance with FIG. 2b, the total torque Mg is also conducted via a converter clutch output 64 to the torsional vibration damping arrangement 10 ', here to a guide plate 59 of a radially inner spring set or inner spring set 58 which is connected in a torque-proof manner to the converter clutch output 64.
- the guide plate 59 can also be regarded as the input region 16 of the torsional vibration damping arrangement 10 '.
- the total torque Mg is divided into a first torque Mg1 and a second torque Mg2.
- the first torque Mg1 passes from the guide plate 59 to an NEN inner spring set 58.
- the first torque Mg1 is passed via a hub disc 61 to an outer spring set 57, which is arranged radially further outward relative to the inner spring set 58 within the converter housing 95.
- the first torque Mg1 passes through a stop element 65 and an intermediate element 52, which is exemplified here as a drive hollow gear carrier of the planetary gear or the coupling assembly 20 and rotatably connected to the stop element 65, to a Antriebshohlrad 68, which in turn rotatably is connected to the Antriebshohlradisme 52 and is rotatable about an axis A.
- the drive gear 68 meshes with a first gear segment 81 -1 of a planetary gear 34 and thus guides the first torque Mg1 to the planetary gear 34.
- the second torque Mg2 passes via the guide plate 59 to a drive sun gear carrier 17 connected in a rotationally fixed manner to the guide plate 59.
- a drive sun gear 28 is attached in a rotationally fixed manner to the drive sun gear carrier 17.
- the drive sun gear carrier 17 and the drive sun gear 28 can also be manufactured as one component.
- the second torque Mg2 is supplied to the drive sun gear 28.
- the drive sun gear 28 meshes with a second gear segment 81 -2 of the planetary gear 34 and thus guides the second torque Mg2 to the planetary gear 34.
- the first torque Mg1 and the second torque Mg2 are brought together again at the planetary gear 34.
- a vibration component in the first torque Mg1 which is passed through the first torque transmission path 18-1 through the phase shifter assembly 42, by means of the phase shift in the ideal case by 180 ° to the vibration component in the second torque Mg2, which is not passed through the phase shifter 42, phase-shifted , Consequently, in the ideal case, the first torque Mg1 would destructively overlap at the planetary gear 34 with a vibration component phase-shifted by 180 ° and the second torque Mg2, so that the total torque Mg without torsional vibration component is applied to an output-side planetary gear carrier 24.
- the planet carrier 24 can also be regarded here as the output region 40 of the torsional vibration damping arrangement 10 '.
- the Planentenradffy 24 is rotatably connected according to Figure 2a, b, c with an output flange 86 to which in turn a transmission input shaft, not shown here, can be rotatably coupled and the total torque Mg, ideally without vibration components, to a transmission, not shown, forward.
- a turbine wheel 75 is non-rotatably connected via a carrier riveted to the intermediate element 52, which is thus non-rotatably connected to the intermediate element 52 the intermediate member or the Antriebshohlradly 52 coupled.
- additional masses 76 coupled to the carrier 71 can be provided which increase the mass moment of inertia of the intermediate element 52 or the secondary side of the phase shifter 42 and thus have a positive effect on the phase shift.
- the turbine wheel 75 of the torque converter 90 also forms a connection to a thrust bearing part 72.
- an additional thrust bearing 72 is inserted between a thrust washer 77 and the output flange 86, so that one additionally rotates with the turbine wheel 75 connected bearing disk 78 between rolling elements of the bearing 72 is guided axially.
- a stator 66 which is non-rotatably connected to the pressure plate 77, guaranteed, but also in addition an axial bearing of the turbine 75 and the components attached thereto, both with respect to the output flange 86, as compared to a freewheel 91 of the Leitrads 66 and the converter housing 95 reaches.
- a plain bearing or a differently designed rolling bearing would also be possible as thrust bearing 72.
- the axial bearing parts 72 should, however, essentially absorb the axial forces of the turbine wheel 75 during converter operation and define the axial position of the intermediate element or the drive hollow wheel carrier 52.
- a radial bearing of the coupling arrangement 20, 30 takes place here via the toothed segments 81 -1, 81 -2 of the planetary gear 34 as so-called flying bearing.
- a central axis B forms a rotary and central axis both for the toothed segment 81 - 1 as well as for the gear segment 81 -2.
- the two gear segments 81 -1 and 81 -2 partially overlap axially (ie in the direction of the axis of rotation A or B), so that the toothed segments 81 -1 and 81 -2 can be performed with 180 degrees each.
- the use of the planetary gear 34 with two different, partially axially overlapping toothed segments 81 -1 and 81 -2 is possible because a rotation angle about the rotational axis B of the planetary gear 34 is sufficiently low.
- the amount of stationary translation increases compared to a transmission with known planetary gears at the same off - and dimensions.
- the two toothed segments 81 -1 and 81 -2 of the planetary gear 34 may also, as shown, partially offset axially relative to each other.
- a total torque Mo via the converter housing 95 and a connecting plate 67 is further passed to a pump 74 of the torque converter 90.
- the impeller 74 rotationally fixed, for example by means of a welded connection, connected to the connecting plate 67.
- the connecting plate 67 is in turn rotationally fixed, for example by means of a welded joint, with the transducer housing 95, respectively.
- the torque converter 90 thus applies the total torque Mo to the impeller 74.
- a torque Mt is applied to the turbine wheel 75.
- the torque Mt is forwarded from the turbine 75 to the intermediate element 52.
- the torque Mt is divided into two torque components Mt1 and Mt2.
- the one torque component Mt2 is applied to the drive ring gear 68, which is non-rotatably coupled to the intermediate element 52.
- the other torque component Mt1 is guided via the intermediate element 52 and the stop element 65 to the outer spring set 57.
- this Drehmomentanteii Mt1 passes via the hub disc 61 to the inner spring set 58 and further from the inner spring set 58 via the ceremoniessbieche 59 to the drive sunradsammlung 1 7 and consequently to the Antriebssonnenrad 28. Since both the Antriebssonnenrad 28 and the Antriebshohlrad 68 mesh with the planetary gear 34, the two torque components Mt1 and Mt2 are brought together again at the planetary gear 34.
- the output side planet carrier 24, on which the planet gear 34 is rotatably mounted the converged torque t to the drive flange 86, the rotation, for example by means of a welding ßharm, connected to the planet carrier 24, forwarded. It is also possible to design the output-side output flange 86 and the planet carrier 24 as an output-side component. From the output-side output drive 86, the combined torque Mt can be forwarded to a transmission, not shown here or a similar component.
- the portion 81 -2 of the planetary gear 34 which meshes with the sun gear 28, not use the space indicated by the reference numeral 80 radially inside the inner spring set 58 and the associated cover plates, if its axis of rotation B, as shown, is parallel to the axis of rotation A of the transducer 90 and when the pivoting range of the planet 34 exceeds a certain angle, otherwise it comes to colliding with the torsion damper 1 0 '. This counteracts the need for ever smaller space.
- embodiments provide a torsional vibration damping arrangement for a drive train of a motor vehicle.
- the torsional momentum comprises an input region to be driven for rotation about a first axis of rotation and an output region.
- the torsional vibration damping arrangement comprises a first torque transmission path extending from the input region to the output region and a second torque transmission path extending from the input region to the output region.
- the torsional vibration damping arrangement further has a coupled to the output range or coupled coupling arrangement for superimposing guided over the two torque transmission paths torques, wherein the coupling arrangement according to embodiments, a planetary gear with at least one planetary gear, which is rotatable about a second axis of rotation.
- the first axis of rotation and the second axis of rotation run obliquely, ie, not parallel to one another.
- the second axis of rotation of the planetary gear of the coupling arrangement with respect to the first axis of rotation of the transmission.
- the second axis of rotation relative to the first axis of rotation can be tilted such that a space radially within the above-described inner spring set of the torsional vibration damping arrangement and the associated cover or guide plates can be better used.
- Vermitte is corresponding inclination or tilt, the radially inner sun gear on its sun gear axially closer to the inner spring set or its guide plates are built, which for the torsional vibration damping arrangement and in particular the torsional vibration damping arrangement comprehensive starting elements can be built axially narrower.
- the first and the second rotation axis are tilted relative to each other such that the first and the second rotation axis extend obliquely in a plane spanned by the two axes of rotation.
- the second rotary axis comprises axis next to an axial component parallel to the first axis of rotation an additional directional component, which is oriented perpendicular to the axial direction defined by the first axis of rotation. This can be for example a radial component.
- an angle between the two axes of rotation may be in a range of 0 ° to 45 °, in particular of 5 ° to 20 °.
- an inclination or tilting of the two axes of rotation is selected such that a radially inner part of the planetary gear or a sun with it meshed sun gear axially closer together with the input area or a (inner) spring set the torsional vibration damping arrangement.
- a rotation axis of a drive gear of the planetary gear located in the first torque transmission path meshing with the planetary gear and a rotation axis of a sun gear of the planetary gear meshing with the second torque transmission path meshing with the planet gear may be parallel to the first rotation axis.
- the planetary gear may include a first planetary gear part having a first gear diameter and a second planetary gear part having a second gear diameter different from the first one.
- first and second Planetenradteil according to some embodiments by different arranged coaxially along the second axis of rotation planetary gears can be realized with different gearing diameters, embodiments may also be preferred in which the first Planetenradteil by a first circular segment of the planetary gear with the first gearing diameter and the second Planetary gear is formed by a second circular segment of the planetary gear with the second gear diameter.
- the latter embodiments efficiently enable a significant axial space gain.
- the different gear diameters of the first and the second Planetenradteils gear ratios between the first torque transmission path and the second torque transmission can be made variable, which can be advantageous to the design of the entire torsional vibration damping arrangement and thereby can provide a space advantage.
- a drive tube located in the first torque transmission path of the planetary gear with the first Planetenradteil and located in the second torque transmission path sun gear of the planetary gear with the second Planetenradteil are in mesh.
- the two planetary gear parts may be arranged axially (i.e., in the respective axial direction) offset relative to one another in the direction of the first and / or the second rotational axis.
- the two Planetenradmaschine in the axial direction, d. H. in the direction along the first and / or the second axis of rotation are arranged in the same axial plane.
- Such embodiments allow in particular a simple and cost-effective production of the planetary gear.
- the first torque transmission path comprises a phase shifter arrangement for generating a phase shift of rotational irregularities conducted over the first torque transmission path with respect to rotational irregularities conducted via the second torque transmission path.
- a phase shifter assembly which may be constructed in the manner of a vibration damper, ie with a primary side and a compressibility of a spring arrangement with respect to this rotatable secondary side.
- the spring arrangement of the phase shifter arrangement may comprise at least one spring set, which advantageously comprises a helical spring. When using at least two spring sets, these can be arranged both in parallel and in serial mode of action.
- a secondary side of the phase shifter arrangement which is coupled with its primary side via the spring arrangement, can essentially be formed by an integral mass main body to provide a desired mass moment of inertia.
- a desired mass moment of inertia Compared to conventionally multi-part or multi-piece masses and / or additional masses to provide the desired mass moment of inertia offers a one-piece mass body in particular space advantages.
- some embodiments propose to mold a ring gear for meshing with the planetary gear in the secondary-side one-piece grounding body.
- the one-piece grounding body can thus simultaneously serve as a drive ring gear for introducing a torque guided via the first torque transmission path into the planetary gear, in which the two torque transmission paths are brought together before being transmitted via an output-side planetary or ring gear carrier to a torque output of the torsional vibration damping arrangement become.
- the one-piece mass body can continue as a radial support for the (Au Ben) spring set the Phasenschieberanord- tion can be used, whereby conventional components such.
- B. guide plates and stop members for the spring assembly can be saved.
- the ground body may also have in a spring channel projecting webs, which can serve as a spring in the spring arrangement as stops in the circumferential direction (ie tangential to the first axis of rotation).
- the torsional vibration damping arrangement with a starting element such as. As a torque converter coupled.
- the torsional vibration damping arrangement between a converter lock-up clutch and the starting element or the hydrodynamic torque converter can be switched.
- the torque converter is arranged axially outside or adjacent to the torsional vibration damping and that the torsional vibration damping arrangement is coupled to a turbine wheel of the torque converter (non-rotatably), which further comprises a stator with a freewheel having a radial bearing, wherein an axial bearing of the freewheel , with which the freewheel is supported axially against the torsional vibration damping arrangement, is arranged radially outside the radial bearing of the freewheel.
- a power branching provided by exemplary embodiments requires a powerful phase shifter as well as the power splitter gearbox itself for optimum function.
- These two components are generally arranged axially next to each other. arranged nander, since in particular when two-row spring accumulators are used as a phase shifter, nesting in the same axial space is not possible.
- a speed-adaptive absorber which also requires space for a damping mass usually axially adjacent to the spring accumulator, comes here that the axial space especially in the inner radial region, ie in the region of the shaft is needed to allow the connection of planet carrier and sun gear or output ring gear, depending on the circuit variant.
- the secondary side of the phase shifter with the associated components such.
- further exemplary embodiments also provide a motor vehicle having an exemplary torsional vibration damping arrangement.
- Figure 1 is a schematic diagram of a torsional vibration damping arrangement with two planetary gears, which are mounted at the output of a phase shifter assembly;
- Figure 2a shows a torsional vibration damping arrangement in application in connection with a hydrodynamic torque converter;
- FIG. 2b shows a torque curve of the arrangement according to FIG. 2a with the converter clutch closed
- FIG. 2c shows a torque curve of the arrangement according to FIG. 2a with the converter clutch open
- FIG. 3 shows a section through a torsional vibration damping arrangement according to an embodiment
- Figure 4a, b is a sectional view of a segmented planetary gear with two different gear diameters according to an embodiment
- FIG. 5 shows a starting element with a torsional vibration damping arrangement according to a further exemplary embodiment, which is arranged between a torque converter
- FIG. 6 shows a starting element with a torsional vibration damping arrangement according to a further embodiment
- FIG. 7 shows a starting element with a torsional vibration damping arrangement according to an exemplary embodiment with an integral mass base body for providing a mass moment of inertia;
- FIG. 8 shows a starting element with a torsional vibration damping arrangement according to an embodiment with a hub disc, which engages from radially inward to radially outward in a spring arrangement of a phase shifter assembly;
- Figure 9, 10 further embodiments of starting elements with a torsional vibration damping arrangement for obtaining additional axial space
- Figure 1 1 a a torsional vibration damping arrangement according to an embodiment with a torque converter, wherein an axial bearing of a freewheel of a stator of the torque converter is disposed radially outside of the freewheel;
- Figure 1 1 b a further embodiment of the thrust bearing according to Figure 1 1 a;
- FIG. 12 shows a torsional vibration damping arrangement according to a further exemplary embodiment with a torque converter, in which an axial bearing of a freewheel of a stator of the torque converter is arranged radially outside of the freewheel;
- FIG. 13 shows means provided between an output region of a torsional vibration damping arrangement and an output region of a coupling arrangement, which limit a relative rotation between the first output region of the torsional vibration damping arrangement and the output region of the coupling arrangement about the axis of rotation.
- FIG. 3 shows an exemplary embodiment of a torsional vibration damping arrangement 100 which, by way of example, is integrated together with a converter bridging clutch 62 and a hydrodynamic torque converter 90 into a converter housing 95 and forms a starting element.
- the torsional vibration damping arrangement 100 thus forms an assembly of a drive train arranged axially next to or adjacent to the converter 90.
- An output 64 of the converter clutch 62 forms an input region 16 of the torsional vibration damping arrangement 100 to be driven or driven around a first axis of rotation A.
- the torsional vibration damping arrangement 100 also comprises a first torque transmission path 18-1 extending from the input region 16 to the output region 40, and one from the input region 16 to the output region 40 extending second torque transmission path 18-2 and thus provides a power split.
- a coupling arrangement 20 Connected to the output region 40 is a coupling arrangement 20 for superimposing torques conducted via the two torque transmission paths 18 - 1, 18 - 2.
- the coupling arrangement 20 comprises a planetary gear 30 with a planetary gear 34, which is rotatable about a second axis of rotation B, which is arranged radially outwardly of the first axis of rotation A, which may be formed for example by a transmission input shaft.
- FIGS. 2 a, b, c differs from the torsional vibration damping arrangement 10 'according to FIGS. 2 a, b, c, in particular in that the first rotation axis A and the second rotation axis B run obliquely relative to one another. Otherwise, the functions are similar, which is why a repeated detailed explanation of the operation is omitted.
- the reader is referred to the description of Figures 2a - c.
- the term "oblique" can be understood to mean that the first axis of rotation A and the second axis of rotation B in a plane defined by the two axes of rotation A, B. Level obliquely or tilted to each other.
- the two axes of rotation A, B can thus be arranged according to embodiments such that they span a common plane.
- This plane may have an axial component (in the direction of the first axis of rotation A) and a radial component (radially away from the first axis of rotation A toward the second axis of rotation B).
- the two axes of rotation A, B can include an angle other than 0 °.
- the angle enclosed by the two axes of rotation A, B may amount to within a range from 0 ° to 45 °, in particular from 5 ° to 20 °.
- an axis of rotation of a drive ring gear 68 of the coupling arrangement 20 located in the first torque transmission path 18-1, which meshes with the obliquely arranged planet gear 34, can run parallel to the first axis of rotation A.
- a rotation axis of a arranged in the second torque transmission 18-2 sun gear 28 of the coupling assembly 20 which meshes with the inclined planetary gear 34 also parallel to the first axis of rotation A.
- the axes of rotation of the drive sprocket 68 and / or the sun gear 28 may be coupled to the axis of rotation A, e.g. can be formed by a transmission input shaft, coincide.
- sun gear 28 and drive ring gear 68 may be in different axially disposed planes, i. H. in different axially along the axis of rotation A offset planes.
- the sun gear 28 is substantially closer to the radially extending inner guide plates 59 of the inner torsional vibration damper 58 in the axial direction (ie in the direction of axis of rotation A).
- the sun gear 28 may now be in the immediate axial vicinity of a connecting pin 69 between the inner damper guide plates 59 and the bearing flange 17. Especially in radial proximity to the first axis of rotation A thus considerable axial space can be saved.
- an internal toothing of the drive ring gear 68 and / or an external toothing of the sun gear 28 can also be formed obliquely.
- some embodiments provide a planetary gear 34, which a first Planetenradtei! (Above the second axis of rotation B) with a first gear diameter and a second Planetenradtei! (below the second axis of rotation B) with a second, different from the first, gear diameter.
- first Planetenradtei! (Above the second axis of rotation B) with a first gear diameter
- second Planetenradtei! below the second axis of rotation B
- different sized and along the second axis of rotation B axially offset from each other arranged planet gears are conceivable, of which, for example, the larger with the sun gear 28 and the smaller can be in mesh with the Antriebshohlrad 68, preferred embodiments ago that the first planetary party! is formed by a first circular segment of the planetary gear 34 with the first gear diameter and the second planetary gear part by a second circular segment of the planetary gear 34 with the second gear diameter.
- FIG. 4 a shows a possible embodiment of the planetary gear 34 with two different toothed segments 81 -1 and 81 -2 in plan view.
- the central or rotational axis B of the toothed segments 81 -1 and 81 -2 may be the same.
- the respective toothing (circle) segment 81 -1 and 81 -2 executed with 1 80 degrees.
- the toothed segments 81 -1 and 81 -2 can be performed with different degrees, such as the toothed segment 81 -1 with 150 degrees and the toothed segment 81 -2 with 210 degrees.
- the sum of the angular degrees of the toothed segments 81 -1 and 81 -2 can also be less than 360 degrees, but a maximum of 360 degrees.
- FIG. 4b shows a possible planetary gear 34 with two different toothed segments 81-1 and 81-2 in section and in plan view.
- Both gearing Segmentation segments 81 -1 and 81 -2 have the same central axis or axis of rotation B.
- the toothed segment 81 -1 with approximately 90 degrees and the toothed segment 81 -2 may be formed with approximately 100 degrees.
- Both toothed segments 81 -1 and 81 -2 may partly overlap in the axial direction (along the axis of rotation B) (see FIG. 4b, left). It is good to see that comparatively much mass and / or material can be saved by using toothed segments.
- Figures 3 and 4 show how can be saved by ⁇ us enclosuresbei american axial space in torsional vibration damping arrangements and thus coupled start-up elements.
- the axis of rotation B of the planet 34 of the coupling assembly 20 is tilted slightly relative to the axis of rotation A of the transmission.
- the space can be used radially within the inner spring set 58 partially for the sun gear 28 and the corresponding toothed segment 81 -2 of the planet 34, which allows a greater width of the teeth.
- the material does not contribute to the strength or rigidity of the construction, but also causes an additional burden on the surrounding parts.
- the connection of the input ring gear 68 with a separate, located radially within the outer damper 57 connection with the cover plate 52 limits the diameter of the tooth pitch circle and thus also means that the mass of the ring gear 68 ange ⁇ on a radially smaller radius. is ordered and thus does not generate as much mass moment of inertia as on a larger radius.
- the mass moment of inertia on the output side of the radially outer spring accumulator 57 is a critically important factor in terms of power-split reduction in both the quality of the phase shift and the decoupling of the oscillatory components of the torque branch 18-1 routed via the phase shifter 42 significantly influenced.
- better decoupling results can be achieved with high mass moment of inertia and matched spring sets and gear ratios than with low ones.
- the option can also be provided to vary the mass moment of inertia by adding or omitting elements.
- these requirements are already taken into account by connecting existing masses or moments of inertia, such as turbine 75, to the output side of phase shifter 42, and by providing additional additional mass 76, for example in the form of variable sizes a sheet and / or a Massering was provided.
- the conventional manufacturing method mainly riveted together sheet metal parts allows optimal use of space in which as much mass sits on a large radius, only conditionally.
- the additional mass 76 connected as a separate component no force flow takes place, thus the very massively executed additional mass 76 does not contribute to the strength or stiffening of the assembly.
- FIG. 5 A further exemplary embodiment is shown in FIG. 5, which differs in particular from a more compact design of the secondary side of the phase shifter arrangement 42 or of the outer spring set 57 from previously explained embodiments. Furthermore, input or drive ring gear 68 is radially outward an inner diameter of the outer damper 57 is connected to the secondary side of the damper 57, resulting in a higher moment of inertia.
- the first torque transmission path 18-1 may include a phase shifter assembly 42 for producing a phase shift of rotational irregularities directed across the first torque transmission path 18-1 relative to the rotational nonuniformities directed by the second torque transmission path 18-2 include.
- the operation of the phase shifter assembly 42 has already been explained in detail at the beginning, which is why a new explanation is omitted here.
- the phase shifter assembly 42 has a radially outer (outer) spring set 57. This outer spring set 57 couples a primary side formed by the hub disc 61 with a secondary side formed by the intermediate element 52.
- the intermediate element 52 coupled to a stop element 65 is connected to a secondary-side ground body 82, for example by means of a welded connection.
- the integrally formed mass base body 82 In order to increase a moment of inertia of the integrally formed mass base body 82, which can have a positive effect on the phase shift, it is connected via a coupled to the grounding body 82 and from radially outward to radially inwardly extending carrier 71 which is rotatably connected to the grounding body 82, with a turbine wheel 75 of an axially adjacent torque converter arranged rotationally fixed.
- additional masses 76 can also be provided here, which increase the mass moment of inertia of the main body 82 and thus have a positive effect on the phase shift.
- grounding body 82 Much of the mass of the spring set 57 downstream assembly is formed by the one-piece grounding body 82, which may be prepared for example by massive forming or casting.
- the grounding body 82 represents a connecting link between the guide plate or intermediate element 52 of the outer spring set 57, which can be constructed simpler than in the original construction according to Figure 2a-c, which allows the modular principle, the moment of inertia of the assembly to various applications adapt.
- a common axially extending rivet 83 connects the components 65, 68, 82 and 76 radially outside an inner diameter of the outer Ren damper 57.
- a Torsionsanschiag 70 which limits a twist angle of the outer spring accumulator 57 and thus protects the spring set 57 against block load, can here preferably be provided between the input side hub disc 61 and the output side guide plate or intermediate element 52 and can the motor side (or torque upstream) from the spring set 57.
- This z. B. on both components 61 and 52 on the motor side corresponding tabs are formed, which overlap to the same extent and thus abut each other after a defined angle of rotation.
- FIG. 6 shows a further optional modification of the construction in which an integration of a ring gear toothing 68a into the one-piece grounding body 82 has taken place.
- An inner diameter of the ground body 82 and thus also the ring gear 68a may be greater than an inner diameter of the outer spring set 57, which leads to a higher moment of inertia.
- the guide plate 52 of the outer spring set 57 may be designed such that it is drawn from the outer spring set 57 next to the latter and between the latter and the ground body 82 radially in the direction of axis of rotation A and with a radially inward-pointing portion on an axial plane surface of the axially adjacent mass body 82 is applied.
- the carrier plate 71 which is arranged axially between the grounding body 82 and an additional mass 76, may be drawn in the axial direction as far as the turbine wheel 75, that is, a connection of the carrier plate 71 to the grounding body 82, the additional mass 76 and, depending on the position on the circumference - either the guide plate 52 or the stop element 65 - for example, by riveting - on a pitch circle with all of the above components axially sweeping rivets is possible.
- Figure 6 also shows an alternative design of the stopper 65 for the protection of the outer spring set 57, wherein radially outwardly bent within the outer spring set 57 and cooperating tabs 84 and 85 of the components 61 and 65 limit a twist angle.
- a bent tab 84 of the primary-side hub disc 61 substantially in the direction of planetary gear 34.
- a corresponding tab 85 of the stop element 65 is formed by a radially inwardly facing end portion of the axially extending beyond stop member 65.
- Other specific designs are of course possible.
- FIG. 7 shows a further optional modification of the construction, in which, in turn, a further functional or component integration has been implemented in order to simplify the use of space, assembly and manufacturability.
- the second axis of rotation B is only slightly tilted or not tilted relative to the first axis of rotation A
- the construction shown in FIG. 7 can readily be combined with exemplary embodiments with first and second axes of rotation A, B running at an angle to each other.
- the one-piece ground body 82 is again preferably produced as a massive forming part. In comparison to other embodiments, the grounding body 82 virtually forms the secondary side of the outer spring set 57 and assumes functions of the intermediate element 52 and stop elements 65.
- the grounding body 82 is here shaped such that it can ensure radial support of the outer spring set 57 as well as in FIG may have the spring channel projecting webs, which provide the springs a stop in the circumferential direction. According to embodiments, the grounding body 82 may thus have in a spring channel of the spring assembly 57 projecting webs, which serve as a spring of the spring assembly 57 as stops in the circumferential direction.
- the spring itself can, as shown in the lower section, in FIG. 7, run in a slide track plate 87, which can be arranged radially within an axial lip of the ground body 82 pointing in the direction of the motor. As a result, the main body 82 can be made simpler, since no spherical contour is necessary.
- the ring gear 68 can again be designed as a separate component and be pressed with the grounding body 82, wherein an additional positive engagement, for example by means of a spline, determine the position and secure against rotation.
- An inner diameter of the grounding body 82 and thus also of the ring gear teeth 68a can again be greater than an inner diameter of the outer spring set 57.
- the spline (also referred to as splines) is a possible shape in a shaft-hub connection. It is a multi-drive connection, whereby the torque is transmitted by the tooth flanks.
- the shaft is external and the hub is internally toothed.
- Other joining or connecting method between grounding body 82 and ring gear 68 or integration as a single component are of course also conceivable.
- a torsion stop for block protection of the outer spring set 57 can be provided such that fingers of the primary side hub disc 61, which reach between the individual springs of the outer spring set 57 in order to drive them, with their tips into an axial groove 88 immerse in the main body 82, which can limit the rotation due to interruptions in the circumferential direction accordingly.
- FIG. 8 shows a further embodiment, which differs from the exemplary embodiments described above in that the primary-side hub disk 61, which is coupled on the input side to the output 64 of the converter lockup clutch 62 and moves radially outward in the direction of the inner spring set 58
- Outer spring set 57 extends, radially engages from the inside out into the outer spring set 57 of the outer torsional vibration damper.
- the guide plate or intermediate element 52 of the outer spring set 57 may be shaped such that it guides the springs axially and radially on the motor side. According to the embodiment shown in Figure 8, the guide plate 52 has a substantially ⁇ -shaped cross-section.
- a stop also at several points in the circumferential direction (for example, between two springs or spring sets connected in series) - segments of the guide plate 52 may be bent radially inward into the spring channel. A separate stop element is therefore not necessary.
- a connection with the grounding body 82 may be, for example, se, as shown, carried out by pressing and / or welding.
- a torsion stop can here, analogous to the embodiment of Figure 6, by mutually corresponding formations on the hub disc 61 and the guide plate 52 done.
- the ring gear 68 and optionally an additional mass 76 by a joining method, such as pressing and / or pinning, be connected to the grounding body 82.
- the inner diameter of the ground body 82 and thus also the ring gear can be significantly larger than an inner diameter of the outer spring set 57.
- the support member 71, which forms the connection to the turbine 75 and the thrust bearing 72 may also be attached to the base 82, for example by pressing and / or welding, as shown in FIG.
- FIGS. 9 and 10 show further embodiments of assemblies with torsional vibration damping arrangements, which are coupled to a torque converter 90.
- the two axes of rotation A, B are not or only slightly tilted to each other, the constructions of Figure 9 and 10 can be combined with exemplary embodiments of the unproblematic in which the two axes A, B obliquely to each other .
- a channel for a fluid (for example oil) which presses an actuating piston 89 against the clutch 62 in order to actuate the clutch 62 is usually formed by beading in the piston carrier 99.
- beads refer to manually or mechanically produced channel-shaped recesses.
- the fluid channel may be in the housing 95 are displaced, so that the piston carrier 89 can be made axially flatter and thereby becomes narrower by the height of the channel.
- the inner spring set 58 can be displaced in the direction of the engine and the result for the transmission 20 is the space gain identified in FIG.
- the rivet 69 can be moved to a radius outside the sun gear top circle for easier assembly and for the radially inwardly facing guide plates 59 of the inner spring set 58 and possibly the hub disc 61 are adjusted.
- FIG. 10 shows a further optional modification of the converter clutch 62, in which, in addition to the above-proposed displacement of the oil passage into the housing 95, the clutch 62 itself is radially outwardly offset so that there is no radial overlap between the converter clutch 62 and the inner spring set 58 or whose guide plates 59 are.
- a point of contact between the actuating piston 89 and the piston carrier 99 can likewise be displaced radially outwards (approximately to the radial height of the inner spring set 58) and axially in the direction of the engine or crankshaft 19.
- the inner spring set 58 can likewise be displaced axially in the direction of the engine and release the additional installation space for the coupling gear 20, 30 marked in FIG.
- the connection of the converter clutch 62 to the spring accumulator, d. H. the clutch output 64 done by appropriate design of the spring accumulator cover plate 59 itself.
- the converter output 64 and the cover plate 59-1 are designed as a single component which can be coupled in a rotationally fixed manner to the hub disc 61 by means of an axial pin 98.
- Another measure which can provide even more axial space for the coupling gear 20, and which will be further explained below, consists in a displacement of the axial bearing point 72 of the freewheel and the phase shifter 42 secondary components.
- FIG. 11 a shows a starting element for a motor vehicle with a torque converter 90 which can be operated via a drive member and a housing arrangement 95 and which has a stator 66 rotatable about an axis of rotation A with a radial bearing 91, 92 comprising a free-wheeling, and an axially disposed outside of the torque converter 90 assembly in the form of a torsional vibration damping arrangement, which has already been explained in detail above.
- the assembly may also have other than the illustrated components.
- the starting element shown in Figure 11a is compared with the embodiments described above, characterized in that an axial bearing or the axial bearing 72 of the freewheel with which the freewheel or the stator 66 is axially supported against the torsional vibration damping arrangement, radially outside of the radial bearing 91, 92 of the freewheel arranged sits.
- the axial bearing 72 of the freewheel can be arranged radially outside of an outer ring 92 of the radial bearing, with which the stator 66 is supported radially against the axis of rotation A and forms the freewheel.
- the axial bearing point 72 laid radially outwards may comprise two axial bearings, which in the force flow between the outer ring 92 of the freewheel or the stator 66 on the one and the planetary gear carrier 24 and .
- An output flange 86 to the transmission input shaft located on the other side and between them still components of the secondary side of the phase shifter 42, such. B. the cover plate 52, the ring gear 68, and optionally the additional mass 76 and the turbine 75 - axially store.
- the thrust bearing 72 is not axially adjacent to the freewheel but radially outward of the freewheel and at least partially the same axial plane.
- the axial bearing 72 of the freewheel may overlap at least partially axially with the radial bearing 91, 92 of the freewheel.
- the space can be released on the motor side next to the freewheel and can be used to, for example, a significantly wider sun gear 28 and / or correspondingly wider tooth segments of a corresponding planet 34 (see Fig. 1 1 a) to realize or to build the transducer 90 as a whole narrower.
- a connection of the turbine 75 to the secondary side of the phase shifter 42 can be realized so that at the radially inner foot of the turbine 75 sheet metal tabs 93 are formed, which passed through corresponding window in the radially inwardly drawn into the thrust bearing 72 cover plate 52 and can then be bent or rolled to connect the two parts 52, 75 form fit with each other.
- the torque converter 90 formed by the turbine wheel 75, the stator 66 and the impeller 74 may be disposed axially adjacent to the torsional vibration damping, wherein the turbine wheel 75 has at least one tab 93 which axially into a driven side member 52 of the torsional vibration damping arrangement engages to rotatably couple the turbine wheel 75 and the torsional vibration damping arrangement or their output area about the axis of rotation A.
- FIG. 11 a results in the following advantages:
- the planet carrier 24 or another output element can be as stiff as possible for optimal performance of the power split. To interpret it on the strength to absorb axial bearing forces, so also benefits its function for the DU reduction. By the additional support point by means of the bearing 72 of the planet carrier 24 itself is additionally stiffened. • The free space above the freewheel is created by an oval design of the hydrodynamic circuit and a higher axial offset between the vanes and freewheel and so far serves to accommodate the masses of a speed-adaptive damper. In the case of DU reduction through power branching, however, this installation space is not needed in the radially inner area and can be usefully used there by laying the bearing point there.
- the component pressure plate 77 can be dispensed with.
- the outer race 92 of the freewheel may be configured to provide a sideways cover (toward the planet carrier 24) and serve as an axial stop for the inner race.
- the outer ring 92 may thus comprise a radially inwardly pointing board, which covers the radial bearing of the freewheel in the direction of the axially adjacent torsional vibration damping arrangement and forms an axial stop for an inner ring of the radial bearing.
- the axial bearing 72 is arranged radially outside the radial bearing 91, 92 and axially between a driven-side component 24 of the assembly (torsional vibration damping arrangement) and a radially extending planar surface of the stator 66.
- a driven-side component 24 of the assembly torsional vibration damping arrangement
- a radially extending planar surface of the stator 66 axially between a driven-side component 24 of the assembly (torsional vibration damping arrangement) and a radially extending planar surface of the stator 66.
- an axial plane surface of the stator 66 a running surface for rolling elements of the thrust bearing 72 ready.
- a further mating surface is provided by a plane surface of the planet carrier 24.
- a radially inner end of the intermediate element 52, on which the rolling elements can roll and which thus acts as a type of bearing disk, is located between the rolling bodies.
- FIG. 11 b shows a further exemplary embodiment of how the bearing 72 can also be designed differently.
- the outer ring 92 of the radial bearing of the freewheel can thus have between its axial ends a radially outwardly facing board 94 which serves as a tread for Rolling the axial bearing 72 of the freewheel is formed.
- the board 94 may thus be arranged between the rolling elements and the axial plane surface of the stator 66.
- FIG. 11 b shows a further exemplary embodiment of how the bearing 72 can also be designed differently.
- the outer ring 92 of the radial bearing of the freewheel can thus have between its axial ends a radially outwardly facing board 94 which serves as a tread for Rolling the axial bearing 72 of the freewheel is formed.
- the board 94 may thus be arranged between the rolling elements and the axial plane surface of the stator 66.
- FIG. 12 shows a further possibility of using the installation space obtained by laying the bearing 72. Due to the space available can also be a circuit of a planetary gear-coupling gear 20 with two ring gears 68, 96, a Antriebshohlrad 68 and a Abreteshohlrad 96, despite the larger axial space requirements can be used without increasing the outer dimensions of the transducer 90.
- the stator 66 is supported via the axial bearing 72 located radially outside the freewheel 91, 92 against a driven hollow wheel carrier 96 coupled to the output flange 86 to the transmission input shaft.
- the stator 66 can be supported via the axial bearing 72 against the planetary and / or Abreteshohlradmay 52, 96 extending radially outwardly from the axis of rotation A.
- the radially outwardly extending planetary and / or Abreteshohlradong 24, 96 form a running surface for rolling elements of the axial bearing 72 of the freewheel.
- FIG 13 another implementation in combination with a coupling transmission circuit with output ring gear instead of planet (carrier) is shown.
- the addressed stop can be implemented, for example, in the form that from the guide plate 52, a tab 97 can be formed, which can engage axially in a corresponding thereto slot in the carrier 96 of the output ring gear.
- sections of the output region 52 of the torsional vibration damping arrangement or of the guide plate 52 and of the output region of the coupling arrangement 20, 30 or of the output hollow wheel carrier 96 overlap in the radial direction.
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- Mechanical Engineering (AREA)
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Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102013214352.4A DE102013214352A1 (de) | 2013-07-23 | 2013-07-23 | Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Kraftfahrzeugs |
PCT/EP2014/063128 WO2015010839A1 (de) | 2013-07-23 | 2014-06-23 | Drehschwingungsdämpfungsanordnung für den antriebsstrang eines kraftfahrzeugs |
Publications (1)
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EP3025070A1 true EP3025070A1 (de) | 2016-06-01 |
Family
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Family Applications (1)
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EP14731662.4A Withdrawn EP3025070A1 (de) | 2013-07-23 | 2014-06-23 | Drehschwingungsdämpfungsanordnung für den antriebsstrang eines kraftfahrzeugs |
Country Status (5)
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US (1) | US20160160957A1 (de) |
EP (1) | EP3025070A1 (de) |
CN (1) | CN105452709B (de) |
DE (1) | DE102013214352A1 (de) |
WO (1) | WO2015010839A1 (de) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102013215726A1 (de) * | 2013-08-09 | 2015-02-12 | Zf Friedrichshafen Ag | Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs |
EP3108153A1 (de) * | 2014-02-19 | 2016-12-28 | Schaeffler Technologies AG & Co. KG | Drehmomentübertragungseinrichtung |
DE102014212825A1 (de) * | 2014-07-02 | 2016-01-07 | Schaeffler Technologies AG & Co. KG | Drehschwingungsdämpfer |
WO2016047660A1 (ja) * | 2014-09-25 | 2016-03-31 | ユニプレス株式会社 | ダイナミックダンパ |
DE102015224762A1 (de) * | 2015-01-22 | 2016-07-28 | Schaeffler Technologies AG & Co. KG | Drehschwingungsdämpfer |
FR3039238B1 (fr) * | 2015-07-24 | 2018-03-02 | Valeo Embrayages | Dispositif d’amortissement de torsion pour un systeme de transmission de vehicule automobile |
JP6344357B2 (ja) * | 2015-09-30 | 2018-06-20 | マツダ株式会社 | 遠心振子ダンパ付き動力伝達装置 |
USD806132S1 (en) * | 2015-11-09 | 2017-12-26 | Eaton Corporation | Spring slider |
DE102015223886A1 (de) | 2015-12-01 | 2017-06-01 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendeleinrichtung |
DE102016211954A1 (de) * | 2016-06-30 | 2018-01-04 | Zf Friedrichshafen Ag | Drehmomentübertragungsvorrichtung |
US10151373B1 (en) | 2017-06-09 | 2018-12-11 | GM Global Technology Operations LLC | Planetary damper architecture with centrifugal pendulum absorber |
US10955025B2 (en) * | 2018-05-31 | 2021-03-23 | GM Global Technology Operations LLC | Vehicle powertrain variable vibration absorber assembly |
US11898625B1 (en) | 2023-01-12 | 2024-02-13 | Schaeffler Technologies AG & Co. KG | Stator assembly |
Family Cites Families (9)
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US3966032A (en) * | 1975-06-09 | 1976-06-29 | General Motors Corporation | Hydrodynamic drive and slipping clutch |
JP3103779B2 (ja) * | 1996-11-22 | 2000-10-30 | 建治 三村 | 差動装置 |
DE19726477A1 (de) * | 1997-06-21 | 1998-12-24 | Mannesmann Sachs Ag | Torsionsschwingungsdämpfer mit bewegbaren Massen |
DE19946333A1 (de) * | 1998-10-05 | 2000-04-06 | Luk Getriebe Systeme Gmbh | Drehmomentwandler |
DE10393579D2 (de) * | 2002-11-14 | 2005-07-07 | Luk Automobiltech Gmbh & Co Kg | Vorrichtung zur Kopplung zweier Wellen |
DE10343906A1 (de) * | 2003-09-19 | 2005-04-28 | Voith Turbo Kg | Überbrückungsschaltung für hydrodynamische Komponenten |
DE502006009337D1 (de) * | 2005-10-29 | 2011-06-01 | Schaeffler Technologies Gmbh | Drehschwingungsdämpfungseinrichtung |
EP2577103B1 (de) | 2010-05-25 | 2019-11-06 | ZF Friedrichshafen AG | Hydrodynamische kopplungseinrichtung, insbesondere drehmomentwandler |
DE102011077119A1 (de) * | 2011-06-07 | 2012-12-13 | Zf Friedrichshafen Ag | Antriebssystem für ein Fahrzeug |
-
2013
- 2013-07-23 DE DE102013214352.4A patent/DE102013214352A1/de not_active Withdrawn
-
2014
- 2014-06-23 WO PCT/EP2014/063128 patent/WO2015010839A1/de active Application Filing
- 2014-06-23 US US14/907,522 patent/US20160160957A1/en not_active Abandoned
- 2014-06-23 EP EP14731662.4A patent/EP3025070A1/de not_active Withdrawn
- 2014-06-23 CN CN201480041650.9A patent/CN105452709B/zh not_active Expired - Fee Related
Non-Patent Citations (2)
Title |
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None * |
See also references of WO2015010839A1 * |
Also Published As
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DE102013214352A1 (de) | 2015-01-29 |
CN105452709B (zh) | 2017-07-04 |
CN105452709A (zh) | 2016-03-30 |
WO2015010839A1 (de) | 2015-01-29 |
US20160160957A1 (en) | 2016-06-09 |
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