DE102013220417A1 - Damper device for a drive train of a motor vehicle - Google Patents

Damper device for a drive train of a motor vehicle

Info

Publication number
DE102013220417A1
DE102013220417A1 DE201310220417 DE102013220417A DE102013220417A1 DE 102013220417 A1 DE102013220417 A1 DE 102013220417A1 DE 201310220417 DE201310220417 DE 201310220417 DE 102013220417 A DE102013220417 A DE 102013220417A DE 102013220417 A1 DE102013220417 A1 DE 102013220417A1
Authority
DE
Germany
Prior art keywords
device
damper device
absorber
dv
damper
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.)
Pending
Application number
DE201310220417
Other languages
German (de)
Inventor
Thomas Dögel
Uwe Grossgebauer
Andreas Orlamünder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Priority to DE201310220417 priority Critical patent/DE102013220417A1/en
Publication of DE102013220417A1 publication Critical patent/DE102013220417A1/en
Pending legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression 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
    • F16F15/1407Suppression 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
    • F16F15/1414Masses driven by elastic elements
    • F16F15/1421Metallic springs, e.g. coil or spiral springs
    • F16F15/1428Metallic springs, e.g. coil or spiral springs with a single mass
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/121Suppression 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 using springs as elastic members, e.g. metallic springs
    • F16F15/123Wound springs
    • F16F15/12353Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations 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
    • F16H2045/0226Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations 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
    • F16H2045/0263Combinations 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 pendulum
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284Multiple disk type lock-up clutch

Abstract

The present invention relates to a damper device for a drive train of a motor vehicle, comprising a starting device, preferably a hydrodynamic torque converter, and a rotatable about a rotation axis Tilgereinrichtung, in particular torsional vibration damping arrangement, with a radially deflectable absorber mass, wherein at least one element of the starting device with the absorber device coupled and is coupled, so that the at least one element of the starting device causes an increase in the absorber mass, wherein the at least one element of the starting device is connected to the absorber mass.

Description

  • The invention relates to a damper device for a drive train of a motor vehicle, comprising a starting device, preferably a hydrodynamic torque converter, and an absorber device rotatable about an axis of rotation, in particular a torsional vibration damping device having a damper mass which can be deflected in the circumferential direction and a return device for the absorber mass, which is substantially radially adjacent to Absorber mass is arranged.
  • The invention also relates to a motor vehicle with a damper device and a drive train of a motor vehicle with a damper device.
  • Although applicable to any damper devices, the present invention will be described in terms of variable fixed frequency dampers.
  • From the DE 10 2012 214 680 A1 a damper device has become known in which a turbine arrangement for selective torque-locking connection of the input side to the output side is arranged. The damper device further comprises a rotational mass on which a mass filter is arranged which comprises an absorber mass. The absorber mass is in turn rotatably mounted by means of a spring system coaxial with the rotational mass. The mass filter is further connected to a turbine arrangement, in particular with a turbine wheel.
  • From the DE 10 2010 054 249 A1 a device for damping vibrations has become known with two damper assemblies and a damper damper. The damper damper thereby comprises two side windows, one extending between damper damper and a hydrodynamic component and with an element of the hydrodynamic component, here the turbine wheel, rotatably connected below the effective diameter of the damper assemblies and the absorber damper.
  • From the DE 10 2011 017 661 a torque transmission arrangement for the drive train of a vehicle has become known in which a turbine wheel forms part of a mass arrangement of a spring-mass pendulum unit, wherein the turbine wheel can be coupled to the output area or to an intermediate mass order.
  • From the DE 10 2011 006 533 Further, a hydrodynamic torque converter has become known, in which a first damper device can perform a circumferential vibration for damping. A cover-plate-like coupling element thereby provides Umfangsabstützbereiche for springs a Tilgeranordnung ready, wherein the coupling element is fixedly connected by welding with a turbine wheel shell of a turbine wheel of a hydrodynamic coupling device.
  • In general, in a damping device in addition to the connection stiffness, which is either for a Festfrequenztilger constant or speed-dependent for a Ordnungstilger, an absorber mass required that takes up a space and requires weight. The already known vibration reduction systems such as a two-damper converter with speed-adaptive absorber make full use of the available space between engine and transmission.
  • In 1 an already known vibration reduction system in the form of a variable Festfrequenztilgers is shown. The variable Festfrequenztilger includes as starting element AE a hydrodynamic torque converter. In the housing or rotating wet space of the same or thus rotating is a pump 27 intended. Opposite this axially is a turbine wheel 32 intended. Between the pump and turbine wheel 27 . 32 is generally denoted by the reference numeral 29 designated stator. Parallel to the hydrodynamic torque transmission path, which is the fluid circulation between impeller 27 , Turbine wheel 32 and stator 29 is a torque transmission path via a lock-up clutch 3 . 4 furnishable. On the lock-up clutch 3 . 4 follows a first stiffness and a second stiffness in the form of torsional vibration dampers 8th . 10 , between which an intermediate mass 9 is formed. At this is a carrier 16 coupled in the form of a drive pulley a Tilgereinrichtung TE. The turbine wheel 32 is right on a hub 14 via a connection 33 stored.
  • The torque flow from the drive to the output leads from the engine via a converter cover 1 , Fins of a lock-up clutch 4 , a toothed ring 5 , and over a spacer 6 on a hub 7 the first stiffness 8th , which is designed in the form of a arranged and acting in the tangential direction helical compression spring set. About a cover plate 9 as an intermediate mass 9 the torque is further to the second, radially inward stiffness 10 headed, whose hub 13 and finally to the hub 14 , which have a hub toothing 15 is tangentially positively connected to a transmission input shaft, not shown. At the intermediate mass 9 , what a 1 designed as a cover plate is the drive disc 16 the absorber TE connected. This absorber TE As inertia mass or inertia, the mass inertia has only the clamping ring 17 to disposal.
  • An object of the present invention is therefore to provide a damper device that allows an increase in the absorber mass and at the same time requires no additional space. Another object of the present invention is to provide an alternative damper device.
  • The present invention solves the problems in a damper device for a drive train of a motor vehicle, comprising a starting device, preferably a hydrodynamic torque converter, and an about a rotation rotatable Tilgereinrichtung, in particular torsional vibration damping arrangement, with a circumferentially deflectable absorber mass and a restoring device for the absorber mass, characterized in that at least one element of the starting device is coupled and / or coupled to the absorber device such that the at least one element of the starting device causes an increase in the absorber mass, wherein the at least one element of the starting device is connected to the absorber mass.
  • The present invention also achieves the objects in a motor vehicle having a damper device in that the damper device according to one of claims 1 to 15 is formed.
  • The present invention further solves the problems in a drive train of a motor vehicle with a damper device in that the damper device is designed according to one of claims 1 to 15.
  • By coupling at least one element of the starting device with the absorber device and the connection of the at least one element of the starting device to the absorber mass is on the one hand causes an increase of the absorber mass, on the other hand, the space is optimally utilized. The absorber device thus utilizes components of the starting element that are present for the absorber mass, for example when driving, when the starting device is closed by means of a conversion lockup clutch and acts as primary inertia. The primary inertia without the connected element of the starting device is in driving, so at speeds well above the starting and idling speed, for a smooth engine no longer required, so it is used as absorber mass.
  • By the terms "first", "second", etc., with respect to a damper device is meant the order of the damper device with respect to the torque flow. A first damper device is so far arranged in the torque flow in front of a second damper device.
  • The term "hub" is to be understood in the broadest sense a rotational mass which is slidable or can be arranged on a shaft or axle and is transmitted to the torque or power from the shaft or axle or is transferable.
  • The term "connecting element" is to be understood in the broadest sense and includes in particular not only elements which are each connected to other elements, but preferably also their connection per se: Thus, for example, a connecting element may be formed as a sheet metal, which is welded to other elements , Likewise, the connecting element may also be a welded connection per se, when the two elements are connected to one another in a material-locking manner via the welded connection.
  • Further features, advantages and preferred embodiments are described in the following subclaims.
  • Advantageously, the restoring device is arranged substantially radially adjacent to the absorber mass. Thus, for example, a provision can be made by means which are not arranged axially or tangentially to the absorber mass.
  • Advantageously, the at least one element of the starting device is connected via a connecting element and in particular via a Tilgerträger the Tilgereinrichtung. Thus, for example, the at least one element of the starting device can also be connected indirectly via a connecting element with the absorber mass. Likewise, the connection of the connecting element, for example via the Tilgerträger done to the absorber mass.
  • Conveniently, the connecting element is connected substantially in the region of the outer radius of the absorber device measured from the axis of rotation. Thus, the connecting element can interact substantially directly with the absorber mass.
  • Expediently, the connecting element is arranged radially further inwards compared with the region of the outer radius of the absorber device on the at least one element of the starting device, in particular substantially at the level of the inner radius of the absorber device. In this way, the connecting element can connect the at least one element of the starting device with the absorber mass in a particularly simple manner. So so the connection element on the one Side at the level of the inner radius of the absorber device to be connected to the at least one element of the starting device and extend to the level of the outer radius of the Tilögereinrichtung. At this height it can then be connected on the other side with the absorber device.
  • Advantageously, a first damper device and an intermediate mass are arranged, in particular wherein a second damper device is connected via the intermediate mass with the first damper device. By arranging further damper means torsional vibrations can be damped in a particularly flexible manner and the damper device can be adapted to a plurality of gears or motors.
  • Conveniently, the absorber device is connected to the intermediate mass, preferably in the region of the radial outer radius of the absorber device. If the absorber device is connected to the intermediate mass in the region of the radial outer radius of the absorber device, this has the advantage that due to the large diameter of the connection, the circumferential forces are smaller, which reduces the load on the respective components. For a particularly simple and direct connection between the at least one element of the starting device and the absorber mass is possible. An extensive in relation to the space connecting element can be omitted, which is axially advantageous for the space.
  • Advantageously, the at least one element of the starting device and the absorber mass are stored together at a position. This allows a simple radial bearing of the at least one element of the starting device and the absorber mass and a very compact in the axial direction space of the damper device.
  • Appropriately, the at least one element of the starting device and the intermediate mass are mounted on the same diameters with respect to the axis of rotation. Among other things, this has the advantage that the respective bearings are the same size and thus cheaper to procure and manufacture. So only a diameter measure for both bearing seats is required.
  • Advantageously, limiting means for limiting a twist angle are arranged in the absorber device, preferably between the intermediate mass and the absorber mass. Limiting means for limiting the angle of rotation can be provided for example in the form of a stop, which is arranged between a cover plate and a clamping ring. This can be used, for example, to protect springs in the absorber, which are designed as leaf springs, from being overloaded by excessive rotation in the circumferential direction.
  • Conveniently, the first damper device and in particular together with the second damper device, connected to a hub which is connected to the absorber device. This allows a simple production of the two damper devices and the connection of the absorber device to the two damper devices.
  • Advantageously, the first damper device is arranged closer to the transmission shaft in the radial direction than the second damper device. Thus, alternatively, the torque flow from the first to the second damper device can take place substantially radially outwards.
  • Conveniently, the damper device is designed such that the absorber device is arranged in its action either in front of or behind the two, in particular in series with each other, damper devices. This has, inter alia, the advantage that due to a lower rigidity of the series connection of the two damper devices, a very good pre-coupling is provided for the absorber device, which improves its mode of action.
  • Advantageously, the intermediate mass is connected via a spacer element with the absorber device. By means of a spacer element can be connected to the intermediate mass, eg. To a common cover plate arrangement of the two damper devices even with a complicated structure of the damper device Tilgereinrichtung.
  • The starting device expediently comprises a turbine wheel as element. Thus, in a simple manner, the turbine adjacent to the drive side of a starting device designed in the form of a hydrodynamic torque converter can be used as an additional mass for the absorber mass.
  • Further important features and advantages of the invention will become apparent from the subclaims, from the drawings, and from associated figure description with reference to the drawings.
  • It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.
  • Preferred embodiments and embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components or elements.
  • In each case show in a schematic form
  • 1 a damper device in the form of an already known variable Festfrequenztilgers;
  • 2 a damper device in the form of a variable Festfrequenz- absorber according to a first embodiment of the present invention;
  • 3 a damper device according to a second embodiment of the present invention;
  • 4 a damper device according to a third embodiment of the present invention;
  • 5 a damper device according to a fourth embodiment of the present invention;
  • 6 a damper device according to a fifth embodiment of the present invention;
  • 7 a damper device according to a sixth embodiment of the present invention;
  • 8th a damper device according to a seventh embodiment of the present invention;
  • 9 a damper device according to an eighth embodiment of the present invention;
  • 10 a damper device according to a ninth embodiment of the present invention;
  • 11 a damper device according to a tenth embodiment of the present invention;
  • 12 a damper device according to an eleventh embodiment of the present invention;
  • 13 a damper device according to a twelfth embodiment of the present invention;
  • 14 a damper device according to a thirteenth embodiment of the present invention;
  • 15 a damper device according to a fourteenth embodiment of the present invention;
  • 16 a damper device according to a fifteenth embodiment of the present invention;
  • 17 a damper device according to a sixteenth embodiment of the present invention;
  • 18 a section through the absorber according to 1
  • 19 an axial section of the absorber of the 18 ; and
  • 20 a half-sectional view of the already known variable Festfrequenztilgers the 1 ,
  • 1 shows a damper device in the form of an already known variable Festfrequenztilgers.
  • In 1 an already known vibration reduction system in the form of a variable Festfrequenztilgers is shown. The variable Festfrequenztilger includes as starting element AE a hydrodynamic torque converter. In the housing or rotating wet space of the same or thus rotating is a pump 27 intended. Opposite this axially is a turbine wheel 32 intended. Between the turbine wheel 32 is generally denoted by the reference numeral 29 designated stator. Parallel to the hydrodynamic torque transmission path, which is the fluid circulation between impeller 27 , Turbine wheel 32 and stator 29 is a torque transmission path via a lock-up clutch 3 . 4 furnishable. On the lock-up clutch 3 . 4 follows a first stiffness and a second stiffness in the form of torsional vibration dampers 8th . 10 , between which an intermediate mass 9 is formed. At this is a carrier 16 coupled in the form of a drive pulley a Tilgereinrichtung TE. The turbine wheel 32 is right on a hub 14 via a connection 33 stored.
  • The torque flow from the drive to the output starts from the engine via a converter cover 1 , Fins of a lock-up clutch 4 , a toothed ring 5 , and over a spacer 6 on a hub 7 the first stiffness 8th , which is designed in the form of a arranged and acting in the tangential direction helical compression spring set. About a cover plate 9 as an intermediate mass 9 the torque is further to the second radially inward stiffness 10 headed, whose hub 13 and finally on the hub 14 , which have a hub toothing 15 is tangentially positively connected to a transmission input shaft, not shown. At the intermediate mass 9 , what a 1 designed as a cover plate is the drive disc 16 the absorber TE connected. This absorber device TE has as absorber mass or inertia, the inertia only the clamping ring 17 to disposal.
  • The following is in the 2 ff. For clarity, in particular only the respective essential differences or relevant components provided with reference numerals.
  • General and especially in the 2 - 17 the first or second damper device can be designed as a "standard damper" or as a "turbine damper" depending on the installation situation. In a "standard damper" the output-side transmission element is rotatably formed with respect to a turbine wheel of a turbine wheel designed as a hydrodynamic clutch assembly damper, whereas in a mounting situation as a "turbine damper" whose Abtriesseitiges transmission element relative to the turbine wheel is relatively rotatable.
  • 2 shows a damper device in the form of a variable Festfrequenztilgers according to a first embodiment of the present invention.
  • In 2 is a variable Festfrequenztilger with use of a turbine of a starter AE shown as additional absorber mass. The structure corresponds essentially to the structure of 1 , In contrast to the structure of 1 is now the turbine wheel 32 over the Tilgerträgerscheibe 21 with the absorber mass 17 connected in the form of the clamping ring, so that their inertia is additionally used as Tilgergägheit. Furthermore, in contrast to 1 is the tangential connection of the turbine wheel 32 to the hub 14 canceled. Only axial force from the stator and turbine axial thrust is up to the support bearing 24 passed; There is no torque transfer to the hub 14 , The connection of the turbine wheel 32 to the clamping ring 17 via the connecting element 34 which extends at the level of the outer radius AR of the absorber device TE up to the level of the inner radius IR of the absorber device TE and at the level of the inner radius IR at the turbine wheel 32 is connected.
  • 3 shows a damper device according to a second embodiment of the present invention.
  • In 3 a two-damper transducer is shown, with the turbine wheel 32 at the level of the outer radius AR directly at the clamping ring 17 connected to this. The absorber device TE is radially inward, ie essentially at the level of the inner radius IR of the absorber device TE, at the intermediate mass 9 is arranged. 3 thus essentially shows an arrangement according to 2 , unlike the 2 the connecting element 21 in the form of the Tilgerträgerscheibe is omitted, since the clamping ring 17 directly at the position 37 with the turbine wheel 32 connected is. This is particularly advantageous for the axial space. The absorber TE is thus as in 2 radially inward at the level of the inner radius IR of the absorber TE with the intermediate mass 9 connected in the form of a cover plate (reference numeral 35 ).
  • 4 shows a damper device according to a third embodiment of the present invention.
  • In 4 is also shown a Zweidämpferwandler, in contrast to 3 the connection of the absorber TE to the intermediate mass 9 in the region of the outer radius AR (reference numeral 36 ) he follows. The absorber system TE is here in particular via the Tilgerträger 16 in the form of the drive disc with the intermediate mass 9 connected. Advantage over the embodiment of 3 is that because of the large diameter of the connection 36 the circumferential forces are smaller and thus the material load decreases. The connection 36 can be designed as cohesive connection, for example by welding, as a positive connection, for example by means of a spline and / or by riveting, screwing or the like and / or via a connecting element. As well as in the 2 and 3 has the turbine wheel 32 no rotatable connection with the hub 14 ,
  • 5 shows a damper device according to a fourth embodiment of the present invention.
  • In 5 is essentially a damper device DV according to 4 shown. In contrast to 4 is in 5 the carrier disk 21 for the clamping ring 17 omitted. Their function is now the starting element in the form of the turbine wheel 32 accepted. This is the turbine wheel 32 , which has the connection 37 with the absorber mass 17 is connected in the form of the clamping ring, rotatably mounted on the storage 38 on the intermediate mass 9 stored in the form of a cover plate. The position of storage 38 in this case lies substantially at the level of the inner radius IR of the absorber device TE in the radial direction below the same. Overall, this allows the axial space along the axis of rotation 2 be reduced.
  • 6 shows a damper device according to a fifth embodiment of the present invention.
  • In 6 is essentially a damper device DV according to 5 shown. In contrast to 5 now takes the storage of turbine wheel 32 and clamping ring 17 together at the position 39 at the hub 14 which lies in the region in the radial direction below the absorber device TE, wherein the hub 14 via a hub toothing 15 With the transmission shaft, not shown, is tangentially positively connected.
  • 7 shows a damper device according to a sixth embodiment of the present invention.
  • In 7 is essentially a damper device DV according to 6 shown. In contrast to the damper device DV according to 6 is according to the damper device DV 7 the storage of the intermediate mass 9 in the form of the cover plate and the storage of clamping ring 17 and turbine wheel 32 axially spaced from each other, but at the same diameter or radius R measured from the axis of rotation 2 arranged, which has the advantage that the bearings are the same size and thus procured cheaper or can be made.
  • 8th shows a damper device according to a seventh embodiment of the present invention.
  • In 8th is essentially a damper device DV according to 6 shown. In contrast to the damper device DV according to 6 is according to the damper device DV 8th an attack 40 between intermediate mass 9 and absorber mass 17 , So arranged between the cover plate and clamping ring to limit the angle of rotation for a Tilgerelement in Tilgereinrichtung TE. For example, absorber elements in the form of Tilgerfedern 18 , Especially designed as leaf springs, these are thereby protected from overloading by a too large angle of rotation.
  • 9 shows a damper device according to an eighth embodiment of the present invention.
  • In 9 are the damper device TE upstream damper devices 8th . 10 now deviating from the 3 to 8th constructed as follows: The radially further outboard first damper device 8th receives the torque over its cover plate 9 from the toothed ring 5 and direct this to her hub 7 further. The hub 7 the first damper device 8th is with two cover plates 12 the second damper device 10 connected, with the cover plates 12 respective spring controls 11 the second damper device 10 wear. At the hub 7 the first damper device 8th is about the connection 36 the drive disk 16 the absorber TE connected. Between the first damper device 8th and the absorber mass 17 is a stop 41 for a Tilgerfeder 18 the absorber TE provided. The storage of the intermediate mass 9 or of the turbine wheel 32 takes place analogously to 8th respectively. 6 ,
  • 10 shows a damper device according to a ninth embodiment of the present invention.
  • In 10 is essentially a damper device DV according to 9 shown. In contrast to the damper device DV according to 9 are in the damper device DV according to 10 the first and second damper means 8th . 10 on a common hub 42 rotatably mounted, on the over the connection 36 the drive disk 16 the absorber device TE is connected. This connection essentially takes place at the level of the outer radius AR of the absorber device TE.
  • 11 shows a damper device according to a tenth embodiment of the present invention.
  • In 11 is essentially a damper device DV according to 8th shown. In contrast to the damper device DV according to 8th is according to the damper device DV 11 the first damper device 8th radially within the second damper device 10 arranged. Both damper devices 8th . 10 have a common intermediate mass 9 in the form of a cover plate arrangement 43 , This is about a spacer 36 the absorber device TE, more precisely its drive disk 16 tethered.
  • 12 shows a damper device according to an eleventh embodiment of the present invention.
  • In 12 is essentially a damper device DV according to 8th shown. In contrast to the damper device DV according to 8th are in the damper device DV according to 12 the first damper device 8th and the second damper device 10 connected in series and thus form a series torsional damper, and the Tilgerträger in the form of the drive disk 16 is no longer like in the 8th at the position 36 Tied to the height of the outer radius AR of the absorber TE, but in the radial direction between the toothed ring 5 and radial bearings 23 , ie, the drive disk 16 is at the position 35 with the hub 14 effectively behind the two damper devices 8th . 10 tethered. This has the advantage that - due to the low rigidity of the series connection of the two damper devices 8th . 10 - Provides a very good pre-decoupling for the absorber TE, which improves their mode of action.
  • 13 shows a damper device according to a twelfth embodiment of the present invention.
  • In 13 is essentially a series torsion damper according to 12 shown, in contrast to the first damper device 8th radially within the second damper device 10 is arranged. The hub 13 the second damper device 10 is now with the Tilgerträger 16 connected in the region of the outer radius AR of the absorber TE.
  • 14 shows a damper device according to a thirteenth embodiment of the present invention.
  • In 14 is essentially a damper device according to 13 shown, wherein the first damper device 8th is omitted and thus the torque directly from the toothed ring 5 on the hub 13 the single damper device 10 is transmitted. The cover sheet 9 is with the Tilgerträger 16 at position 35 connected and also with the toothed ring 5 , The turbine wheel 32 together with the absorber mass 17 is there like in 13 stored. The absorber mass 17 or the clamping ring can be chosen so small in the radial direction that it is at least partially below the damper device 10 can be arranged, which advantageously reduces the axial space.
  • 15 shows a damper device according to a fourteenth embodiment of the present invention.
  • In 15 is essentially a damper device in the form of a torsion damper according to 14 shown. In contrast to the torsion damper according to 14 is in 15 the damper device DV over the cover plate 9 driven, ie the toothed ring 5 is over the cover plate 9 with the single damper device 10 connected. Thus, the (primary) mass of the torsion damper over the execution in the 14 elevated.
  • 16 shows a damper device according to a fifteenth embodiment of the present invention.
  • In 16 is essentially a torsion damper according to 14 shown. Here is the output side cover plate 9 the single damper device 10 at the height of the outer radius AR of the absorber TE with the Tilgerträger 16 or the drive disk directly connected. This allows a waiver of a hub disc, since the drive disc 16 whose function takes over. In this way, axial space can be saved.
  • 17 shows a damper device according to a sixteenth embodiment of the present invention.
  • In 17 a damper device DV is shown in the form of a turbine torsional damper. The structure corresponds essentially to the structure according to 15 , being at the hub 7 the radially outer first damper device 8th now the second damper device 10 is arranged. The cover sheet 12 the second damper device 10 is together with the cover plate 9 the first damper device 8th and the absorber TE at the hub 14 stored. The two damper devices 8th . 10 So are really directly with the hub 14 connected and are therefore like a turbine torsion damper behind the mass of the turbine wheel 32 and thus also behind the absorber TE. As a result, the absorber device TE is connected to the primary side.
  • 18 and 19 show sections through an already known absorber device, 20 by an already known damper direction with a Tilgereinrichtung according to the 18 and 19 ,
  • In 18 is a half-sectional view of an absorber TE shown in an already known embodiment. In 19 is an axial view of the absorber according to 18 shown and in 20 is a half-sectional view according to the already known embodiment according to 1 shown.
  • Such Tilgereinrichtung TE as in the 18 and 19 can be used in the damper device according to the present invention.
  • The 18 shows a generally designated TE Tilger- or torsional vibration damping arrangement, which can be integrated to fulfill the functionality of a speed-adaptive absorber in a drive train of a vehicle or coupled to this. The torsional vibration damping assembly TE includes a carrier to be fixed about a rotational axis A by screwing it to a drive train component for common rotation therewith 44 , In this carrier 44 are in the presentation of 19 At several circumferential positions preferably with approximately uniform circumferential distance guides F provided in which effective as a flow weight support elements 20 are taken radially movable in the form of sliding blocks. The guides F are formed as substantially radially extending, slot-like recesses, which radially inward through a radially inner base position of the support elements 20 defining stops 45 are limited. The support elements 20 are formed by designed as a particular conical helical compression springs biasing springs 19 radially inward to rest against the stops 45 , thus kept biased in their and in their base situation. They support the bias springs 19 on a radially outer annular edge region of the carrier 44 from.
  • On the carrier 44 is about a radial bearing 46 and a thrust bearing 47 a carrier disk 28 about the axis of rotation A with respect to the carrier 44 basically rotatable. In its radially outer region carries the carrier disk 21 for example, by screwing on one axial side of a mass ring 17 , On the other axial side, for example, another mass ring can be defined. The carrier disk 21 forms together with the mass ring 17 and possibly also the further mass ring a deflection mass. Passing through a plurality of circumferentially elongated recesses and an axial securing ring 48 at the of the carrier 44 opposite side of the carrier disk 21 holding bolts 49 , For example, bolt, is the carrier disc 21 and thus the deflection mass axially on the carrier 44 secured. By the circumferential movement clearance of the bolt 49 in the recesses of the carrier disc 21 is the deflection mass in a corresponding circumferential motion clearance with respect to the carrier 44 around the axis of rotation 2 rotatable, so that by cooperation of the bolts 40 is provided with the recesses a relative rotation angle limiter.
  • The deflection mass is with the carrier 44 by a plurality of circumferentially successive, substantially radially extending return elements 18 coupled to the power transmission. These here, for example, as leaf springs or generally designed as a bending beam reset elements 18 are in their rardial outer area by a respective clamping arrangement at Massering 17 established. Starting from this definition, they extend radially inward through openings in the edge region of the carrier 44 through into a respective biasing spring 19 into it.
  • The or each return element 18 with its radially inner end region into a central opening of an associated support element 20 into or through it. In the area of the central opening 52 are on the support element 20 at a lateral distance zueinaner two, for example, on pins 50 . 51 provided Umfangsabstützbereiche provided.
  • These Umfangsabstützbereiche, which in the circumferential direction on both sides of the radially inner end portion of the associated return element 18 lie, define in their entirety a Trägerabstützbereich 52 whereas in the region in which the radially outer end region of the return element 18 at the Massering 30 or the deflection mass is generally defined, a Auslenkungsmassenabstützungsbereich 53 is formed.
  • As explained below, the reset element 18 received with movement play between the two Umfangsabstützungsbereichen to a centrifugal force auftregende radial movement of the support element 20 in the associated guide F in the carrier 44 to enable. At this radial movement, a tilting of the support element 20 To prevent this has on its two axially oriented sides guide projections which in associated, substantially radially extending guide recesses of the carrier 44 or the carrier disk 21 extend and are radially movably guided or received therein. In particular by interaction of the guide projection with the carrier disk 21 their relative rotation with respect to the carrier 44 not to affect their recesses may have a greater circumferential width, as the recesses in the carrier 44 , Next can occur under centrifugal force tilting of the support element 20 be prevented that its center of gravity is approximately centrally in the central opening.
  • In the foregoing with reference to the 18 to 20 In terms of their structural design explained torsional vibration damping arrangement TE forms each one in the carrier 44 radially movable guided support 20 That with this cooperating return element 18 that the support element 20 radially biasing into its recognizable base position biasing bias spring 19 and the deflection mass each comprise a deflection mass pendulum unit 54 , In this case, in the illustrated embodiment, a total of ten such Auslenkungsmassenpendeleinheiten 54 provided, the carrier 44 a common carrier 44 for the support elements 20 all deflection mass pendulum units 54 is and the Auslenkungsmasse a common deflection mass for all Auslenkungsmassenpendeleinheiten 54 is. However, in principle, the principles could also be realized when associated with each or at least part of the deflection mass pendulum units 54 a separate carrier is provided and / or when in association with all or part of the Auslenkungsmassenpendeleinheiten 54 an independent deflection mass is provided. For reasons of stability and to avoid unwanted vibration states or to obtain a synchronous vibration behavior of all Auslenkungsmassenpendeleinheiten 54 However, at least the cooperation of all Auslenkungsmassen to a common, annular deflection mass is advantageous.
  • In summary, the present invention provides, inter alia, the advantage that by connecting an element of a starting device an increase in the absorber mass of a Tilgherreichtung can be achieved without this the space, in particular the axial space must be increased.
  • Although the present invention has been described above with reference to preferred embodiments, it is not limited thereto, but modifiable in many ways.
  • LIST OF REFERENCE NUMBERS
  • 1
     converter cover
    2
     axis of rotation
    2a
    spigot
    3
     Wheels of Wanderlüberbrückungskupplung
    4
     Slats of the lockup clutch
    5
     toothed ring
    6
     spacer
    7
     Hub disc C1
    8th
     First stiffness ("C1") / first damper device
    9
     Cover plate 1
    10
    Second stiffness ("C2") / second damper device
    11
    spring activation
    12
    Cover plate 2
    13
    Hub disc C2
    14
    Hub on transmission input shaft
    15
    hub profile
    16
    Drive pulley of the absorber
    17
    clamping ring
    18
    Absorber spring / leaf spring
    19
    Sensor spring / conical helical compression spring
    20
    slide
    21
    Carrier disk for clamping ring
    22
    Storage of the clamping ring to carrier disk
    23
    Radial bearing cover plate 1 to hub 14
    24
    Thrust bearing against turbine thrust
    25
    Thrust bearing against stator thrust
    26
    Kolbendrichtungen
    27
    impeller
    28
    Converter neck with spline
    29
    stator
    30
    freewheel
    31
    Leitradstützwelle
    32
    turbine
    33
    Connection of the turbine to the hub 14
    34
    Connection of the turbine to the clamping ring 17
    35
    Connection drive disk radially inside
    36
    Connection drive disc radially outside
    37
    Connection turbine to clamping ring
    38
    Storage of the turbine on cover plate 1
    39
    Storage of the turbine on the hub
    40
    Tailgate stop between clamping ring 17 and cover plate 1
    41
    Tiller stop between actuation disc 16 and clamping ring 17
    42
    Common hub C1 / C2
    43
    Common cover plate C1 / C2
    TE
    Tilgereinrichtung
    DV
    damper device
    AR
    outer radius
    IR
    inner radius
    R
     radius
    F
     guide
    44
    carrier
    45
    attack
    46
    radial bearings
    47
    thrust
    48
    axial securing
    49
    bolt
    50, 51
    pencils
    52
    Trägerabstützbereich
    53
    Auslenkungsmassenabstützbereich
    54
    Auslenkungsmassenpendeleinheit
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 102012214680 A1 [0004]
    • DE 102010054249 A1 [0005]
    • DE 102011017661 [0006]
    • DE 102011006533 [0007]

Claims (17)

  1. Damper device (DV) for a drive train of a motor vehicle, comprising a starting device (AE), preferably a hydrodynamic torque converter, and one about an axis of rotation ( 2 ) rotatable Tilgereinrichtung (TE), in particular torsional vibration damping arrangement, with a deflectable in the circumferential direction Tilgermasse ( 17 ) and a restoring device ( 18 ) for the absorber mass ( 17 ), characterized in that at least one element ( 32 ) of the starting device (AE) with the absorber device (TE) is coupled and / or coupled such that the at least one element ( 32 ) of the starting device (AE) an increase in the absorber mass ( 17 ), wherein the at least one element ( 32 ) of the launch facility (AE) to the absorber mass ( 17 ) is attached.
  2. Damper device (DV) according to claim 1, characterized in that the return device ( 18 ) substantially radially adjacent to the absorber mass ( 17 ) is arranged.
  3. Damper device (DV) according to one of claims 1-2, characterized in that the at least one element ( 32 ) the starting device (AE) via a connecting element ( 34 ) and in particular via a Tilgerträger ( 16 ) of the absorber device (TE) is connected.
  4. Damper device (DV) according to claim 3, characterized in that the connecting element ( 34 ) to the absorber device (TE) substantially in the region of the outer radius (AR) of the absorber device (TE) measured from the axis of rotation (FIG. 2 ) is attached.
  5. Damper device (DV) according to one of claims 1-4, characterized in that the connecting element ( 34 radially inward compared with the region of the outer radius (AR) of the absorber device (TE) on the at least one element (FIG. 32 ) of the starting device (AE) is arranged, in particular substantially at the level of the inner radius (IR) of the absorber device (TE).
  6. Damper device (DV) according to one of claims 1-5, characterized in that a first damper device ( 8th ) and a Zwischasse ( 9 ), in particular wherein a second damper device ( 10 ) over the intermediate mass ( 9 ) with the first damper device ( 8th ) connected is.
  7. Damper device (DV) according to claim 6, characterized in that the absorber device (TE) to the intermediate mass ( 9 ), preferably in the region of the radial outer radius (AR) of the absorber device (TE), is connected.
  8. Damper device (DV) according to one of claims 1-7, characterized in that the at least one element ( 32 ) of the starting device (AE) and the absorber mass ( 17 ) at a position ( 39 ) are stored together.
  9. Damper device (DV) according to one of claims 1-7, characterized in that the at least one element ( 32 ) of the starting device (AE) and the intermediate mass ( 17 ) on equal diameters (R) with respect to the axis of rotation ( 2 ) are stored.
  10. Damper device (DV) according to one of claims 1-9, characterized in that limiting means ( 40 ) for limiting a twist angle for a spring element ( 18 ) of the absorber device (TE) are arranged, preferably between intermediate mass ( 9 ) and absorber mass ( 17 ).
  11. Damper device (DV) according to one of claims 1-10, characterized in that the first damper device ( 8th ) and in particular together with the second damper device ( 10 ), with a hub ( 42 ), which is connected to the absorber device (TE).
  12. Damping device (DV) according to one of claims 1-11, characterized in that the first damper device ( 8th ) in the radial direction closer to the transmission shaft ( 2 ) is arranged as the second damper device ( 10 ).
  13. Damper device (DV) according to one of claims 1-12, characterized in that the damper device (DV) is designed such that the absorber device (TE) in their effect either in front of or behind the two, in particular in series damper devices ( 8th . 10 ) is arranged.
  14. Damper device (DV) according to one of claims 1-13, characterized in that the intermediate mass ( 9 ) via a spacer element ( 36 ) is connected to the absorber device (TE).
  15. Damper device (DV) according to any one of claims 1-14, characterized in that the starting device ( 36 ) as element a turbine wheel ( 32 ).
  16. Motor vehicle with a damper device (DV), characterized characterized in that the damper device (DV) is designed according to one of claims 1-15.
  17. Drive train of a motor vehicle with a damper device (DV), characterized in that the damper device (DV) is designed according to one of claims 1-15.
DE201310220417 2013-10-10 2013-10-10 Damper device for a drive train of a motor vehicle Pending DE102013220417A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE201310220417 DE102013220417A1 (en) 2013-10-10 2013-10-10 Damper device for a drive train of a motor vehicle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310220417 DE102013220417A1 (en) 2013-10-10 2013-10-10 Damper device for a drive train of a motor vehicle
PCT/EP2014/069619 WO2015051976A1 (en) 2013-10-10 2014-09-15 Damping device for a drive train of a motor vehicle

Publications (1)

Publication Number Publication Date
DE102013220417A1 true DE102013220417A1 (en) 2015-04-30

Family

ID=51542370

Family Applications (1)

Application Number Title Priority Date Filing Date
DE201310220417 Pending DE102013220417A1 (en) 2013-10-10 2013-10-10 Damper device for a drive train of a motor vehicle

Country Status (2)

Country Link
DE (1) DE102013220417A1 (en)
WO (1) WO2015051976A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6349966B2 (en) * 2014-05-28 2018-07-04 アイシン精機株式会社 Damper device

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009042837A1 (en) * 2008-10-16 2010-04-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrodynamic torque converter
DE102010054249A1 (en) 2009-12-21 2011-06-22 Schaeffler Technologies GmbH & Co. KG, 91074 Power transmission device
DE102011017661A1 (en) 2010-05-07 2011-11-10 Zf Friedrichshafen Ag Torque transmission arrangement for the drive train of a vehicle
DE102011017660A1 (en) * 2011-04-28 2012-10-31 Zf Friedrichshafen Ag Torque transmitting assembly
DE102012214680A1 (en) 2011-09-29 2013-04-04 Schaeffler Technologies AG & Co. KG Torque converter for transmission of rotational torque between e.g. multi-cylinder reciprocating engine and dual-clutch transmission in passenger car, has damping mass rotatably and coaxially supported with respect to rotation mass

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10236752A1 (en) * 2002-08-10 2004-02-19 Daimlerchrysler Ag Motor vehicle drive train, has spring-mass damper system in parallel with drive train interacting with torsional vibrations with energy exchange with drive train between start-up element, output shaft
DE102012218924A1 (en) * 2012-10-17 2014-04-17 Zf Friedrichshafen Ag Torsional vibration damping arrangement with speed-dependent stiffness
DE102012218921A1 (en) * 2012-10-17 2014-04-17 Zf Friedrichshafen Ag Torsional vibration damping arrangement
DE102012218918A1 (en) * 2012-10-17 2014-04-17 Zf Friedrichshafen Ag Torsional vibration damping arrangement with speed-dependent characteristic

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009042837A1 (en) * 2008-10-16 2010-04-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrodynamic torque converter
DE102010054249A1 (en) 2009-12-21 2011-06-22 Schaeffler Technologies GmbH & Co. KG, 91074 Power transmission device
DE102011017661A1 (en) 2010-05-07 2011-11-10 Zf Friedrichshafen Ag Torque transmission arrangement for the drive train of a vehicle
DE102011006533A1 (en) 2010-05-07 2011-11-10 Zf Friedrichshafen Ag Torque transmission assembly, in particular hydrodynamic torque converter, fluid coupling or wet-running clutch
DE102011017660A1 (en) * 2011-04-28 2012-10-31 Zf Friedrichshafen Ag Torque transmitting assembly
DE102012214680A1 (en) 2011-09-29 2013-04-04 Schaeffler Technologies AG & Co. KG Torque converter for transmission of rotational torque between e.g. multi-cylinder reciprocating engine and dual-clutch transmission in passenger car, has damping mass rotatably and coaxially supported with respect to rotation mass

Also Published As

Publication number Publication date
WO2015051976A1 (en) 2015-04-16

Similar Documents

Publication Publication Date Title
US9803717B2 (en) Centrifugal-force pendulum device
US9360081B2 (en) Torsional vibration damper for hydrokinetic torque coupling device
DE112011102382B4 (en) starter
EP2577108B1 (en) Hydrodynamic coupling device
EP2959181B1 (en) Vibration damper for clutch friction disc of a motor vehicle
US9797471B2 (en) Absorber system
US10100898B2 (en) Torsional vibration damper
US8161739B2 (en) Force transmission device in particular for power transmission between a drive engine and an output
JP5496904B2 (en) Torque converter
US10047844B2 (en) Dynamic damper device
US8690688B2 (en) Double damping flywheel with double damping elements
JP5933166B2 (en) Fluid torque converter
US10125844B2 (en) Torsional vibration damper assembly
US9506524B2 (en) Lock-up device for fluid coupling
DE10362352B3 (en) Torsional vibration damper
US8910762B2 (en) Centrifugal-pendulum vibration absorbing device
US10018262B2 (en) Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
DE3448618C2 (en) Clutch disc with torsional vibration damper
US9556928B2 (en) Rotary vibration damping arrangement
US4810231A (en) Torsional vibration damper having springs with progressive characteristics
JP5538408B2 (en) Hydrodynamic torque converter
KR101358998B1 (en) Torque converter for vehicle
CN105658992B (en) Torsional vibration damper
US9140348B2 (en) Hydrodynamic coupling arrangement, in particular a torque converter
US9752666B2 (en) Torque converter

Legal Events

Date Code Title Description
R163 Identified publications notified