WO2007054053A1 - Hydrodynamische drehmomentwandler-vorrichtung für einen kraftfahrzeug- antriebsstrang - Google Patents
Hydrodynamische drehmomentwandler-vorrichtung für einen kraftfahrzeug- antriebsstrang Download PDFInfo
- Publication number
- WO2007054053A1 WO2007054053A1 PCT/DE2006/001820 DE2006001820W WO2007054053A1 WO 2007054053 A1 WO2007054053 A1 WO 2007054053A1 DE 2006001820 W DE2006001820 W DE 2006001820W WO 2007054053 A1 WO2007054053 A1 WO 2007054053A1
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- WO
- WIPO (PCT)
- Prior art keywords
- component
- energy storage
- storage device
- turbine shell
- driver part
- Prior art date
Links
- 238000004146 energy storage Methods 0.000 claims description 143
- 239000002184 metal Substances 0.000 claims description 5
- 230000005540 biological transmission Effects 0.000 description 9
- 238000003466 welding Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H2045/007—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a damper between turbine of the fluid gearing and the mechanical gearing unit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0284—Multiple disk type lock-up clutch
Definitions
- Hydrodynamic torque converter device for a motor vehicle
- the invention relates to a hydrodynamic torque converter device for a motor vehicle drive train, which has a torsional vibration damper and a transducer torus formed by a pump wheel, a turbine wheel and a stator.
- a hydrodynamic torque converter device for a motor vehicle drive train is already known from FIG. 3 of DE 196 14 411 A1, which has a torsional vibration damper as well as a transducer torus formed by a pump wheel, a turbine wheel and a stator.
- the local torsional vibration damper has exactly one energy storage device which is arranged between an input part and an output part.
- the output member is rotatably connected to a hub, which in turn is rotatably coupled to a shaft.
- the input part is connected to the piston of a converter bridging clutch in such a way that, when the converter lockup clutch is closed, the energy storage device can be loaded by the converter housing via the input part.
- the input part is further coupled via a rivet connection with the outer turbine shell of the converter torus.
- a hydrodynamic torque converter device for a motor vehicle drive train in which the torsional vibration damper has two energy storage devices.
- a driver part is welded, which is connected via a plug connection to the input part of an outer damper or an external energy storage device.
- the output part of this outer energy storage device is in turn coupled to the piston of a lockup clutch and at the same time forms the input part of the inner energy storage device whose output part is connected to a hub.
- Another hydrodynamic torque converter device for a motor vehicle drive train in which the torsional vibration damper has two energy storage devices is known from FIG. 1 of DE 103 58 901 A1.
- the input part of the outer energy storage device is coupled to a converter bridging clutch.
- An intermediate part simultaneously forms the output part of the outer energy storage device and the input part of the inner energy storage device, which is connected via its output part with a hub.
- an extension of the outer turbine shell is supported radially.
- a driver part is welded, which, on the other hand, is coupled to the intermediate part via a connecting means configured as a bolt connection.
- the invention is based on the object of providing a torque converter with a torsional vibration damper and with one of a pump impeller, a turbine wheel and a stator torque converter device provided for a motor vehicle powertrain, which can be produced easily manufactured and the reliable relieve or compensate for rotational shocks an internal combustion engine allows.
- a hydrodynamic torque converter device for a motor vehicle drive train which has a torsional vibration damper and a transducer torus formed by a pump wheel, a turbine wheel and a stator.
- a device referred to herein as a "transducer torus” is sometimes referred to as a "hydrodynamic torque converter”;
- the term “hydrodynamic torque converter” is sometimes used in prior publications for devices comprising a torsional vibration damper, optionally a lockup clutch and a device formed by a impeller, a turbine wheel and a stator or - in the diction of the present disclosure - a transducer torus .
- the terms “(hydrodynamic) torque converter device” and “converter torus” are used in the present disclosure for better distinctness.
- the torsional vibration damper has a first energy storage device with one or more Ren first energy storage and a second energy storage device with one or more second energy storage.
- the first energy storage device is connected in series with the second energy storage device, wherein between these two energy storage devices - also connected in series - a first component is provided.
- the transducer torus has-in particular in the usual form-a torus interior or a torus interior, which is designed in particular substantially torus-shaped or ring-shaped.
- An outer turbine shell forms a directly adjacent to the Torusinnere for the boundary wall section.
- the outer turbine shell is connected to the first component such that a load, such as in particular torque or force, from the outer 'turbine shell is transferable to the first component, wherein along the thus formed load transfer path, via which the load or the torque of the outer turbine shell is transferable to the first component, at least one connecting means is provided, by means of which - in particular adjoining - components for the torque or load transmission are interconnected.
- a connection means may be, for example, a rivet connection or a bolt connection or a screw connection or a welded connection or a plug connection or the like.
- connection means by means of which along the load transfer path between the outer turbine shell and the first component - in particular adjacent - components are connected, are spaced from the immediately adjacent to the Torusinnere or Torusinnenraum for limiting its wall portion of the outer turbine shell.
- turbine blades are provided, which are arranged in a conventional manner in the interior of the torus or Torusinnenraum.
- the addressed connecting means are arranged at a distance from the sections of the outer turbine shell, to which the turbine blades adjoin the outer turbine shell or are formed there.
- the addressed load transfer path between the outer turbine shell and the first component is free of the first and the second energy storage device, so that a torque or a load along this load transfer path from the outer turbine shell to the first component is transferable, without that to be passed over or through one of the energy storage devices before the torque or the load reaches the first component.
- the addressed driver part can be connected via a second connecting means with the second component. It can also be provided in the mentioned load transfer path more than two connecting means.
- the first energy storage device has a plurality of first, circumferentially distributed and spaced apart first energy storage and / or that the second energy storage device distributed a plurality of circumferentially or spaced second energy storage.
- the energy storage must not necessarily be located on an exact circumferential path.
- the first energy storage of the first energy storage device are each Bogenfedem and the second energy storage of the second energy storage device are each straight springs or straight compression springs.
- both the first energy store of the first energy storage device and the second energy store of the second energy storage device are each spiral springs.
- the torque converter device further comprises a lockup clutch.
- the converter lockup clutch is connected on the input side to a converter housing and is coupled on the output side directly or via one or more intermediate components to a second component, so that when the converter lockup clutch is in a torque from the converter housing via the converter lockup clutch to the second component is transferable.
- the second component may, for example, the input part of the first energy be memory device.
- the second energy storage device - connected in series - is arranged between the first component and a third component.
- the third component may, for example, form a hub or be non-rotatably coupled to a hub.
- Such a hub for example, with a shaft, such as transmission input shaft or the like, be rotatably coupled.
- a second component, the first energy storage device, a first component, the second energy storage device and the third component are connected in series. It can be provided that the addressed series circuit consists exclusively of the mentioned components or that one or more parallel or intermediate components are provided.
- the outer turbine shell is arranged pivotable or rotatable relative to the already mentioned hub.
- the outer turbine shell - preferably supported by a sleeve-shaped support portion - radially on the hub.
- This support can be such that essentially no torque can be transmitted from the outer turbine shell to the hub via the mentioned support. It is therefore provided in particular that a torque from the outer turbine shell to the hub substantially via the second energy storage device - but not via an additionally provided, in particular radial, support - can be transmitted from the outer turbine shell to the hub.
- an additional bearing device such as plain bearing bush or roller bearing or the like, is provided between the mentioned support section and the hub.
- the mentioned - in particular sleeve-shaped - support portion may be provided for example on an extension of the outer turbine shell or on a driver part or on a separate support member.
- the outer turbine shell or an extension of the outer turbine shell is connected by means of a driver part with the second component. It can be provided that by means of a first connecting means of the extension is connected to the driver part and by means of a second connecting means, the driver part is connected to the first component. It can also be provided, in particular, that the driver part has an extension on which the energy storage device of the first energy storage device is supported directly.
- the driver part extends from one in the radially inner region of the outer tur- binenschale located portion or extension of the outer turbine shell to the second component.
- the addressed driver part extends from a radially outer portion of the outer turbine shell to the second component.
- the driver part and / or the first component and / or the second component and / or the third component are formed as a metal sheet.
- the driver or driver plate has a greater wall thickness than the second component.
- the driver part-in particular with respect to the axis of rotation of the torsional vibration damper- has a greater mass moment of inertia than the second component. It can also be provided that the mass of the driver part is greater than that of the second component.
- a relative VerFwinkelbegrenzung or VerFwinkelbegrenzung for the torsional vibration damper or for the first and / or second E nergie official est is provided and in particular a Vermoswinkelbegrenzung, which goes into a stop position before the energy storage of the first and / or second energy storage device go to block, provided that they are trained so that they can go to block.
- a rotation angle limitation limits the maximum relative twist angle between the input part and the output part of the relevant energy storage device.
- a rotation angle limitation is provided only for the second energy storage device, ie not for the first energy storage device; It can be provided that the first energy storage arc springs, and the second energy storage are straight (pressure) springs.
- the driver part is connected via first connecting means with the outer turbine shell or an extension of the outer turbine shell and is rotatably connected, wherein the connecting means are provided in a region in which the extension or the outer turbine shell and / or the driver part is straight, and in a particularly preferable embodiment - with respect to the radial direction of the axis of rotation of the torsional vibration damper - in the radial direction - in particular in each case - straight.
- Fig. 1 shows a first embodiment of a hydrodynamic according to the invention
- Fig. 2 shows a second embodiment of a hydrodynamic according to the invention
- Fig. 3 shows a third embodiment of a hydrodynamic according to the invention
- Fig. 4 shows a fourth embodiment of a hydrodynamic according to the invention
- FIGS. 1 to 4 show various embodiments of a hydrodynamic torque converter device 1 according to the invention.
- the hydrodynamic torque converter device 1 is intended for a drive train of a motor vehicle or forms part of a motor vehicle drive train, which is schematically illustrated by the reference numeral 2.
- the hydrodynamic torque converter device 1 has a torsional vibration damper 10, a converter torus 12 formed by an impeller 20, a turbine wheel 24 and a stator 22, and a converter lock-up clutch 14.
- the torsional vibration damper 10, the transducer torus 12 and the lockup clutch 14 are accommodated in a converter housing 16.
- the converter housing 16 is substantially non-rotatably connected to a drive shaft 18, which is for example the crankshaft or engine output shaft of an internal combustion engine.
- the transducer torus 12 has - as mentioned - a pump or an impeller 20, a stator 22 and a turbine or a turbine wheel 24, which cooperate in a conventional manner.
- the transducer torus 12 has a transducer interior space or a torus interior 28, which is provided for receiving oil or for an oil flow.
- the turbine wheel 24 has an outer turbine shell 26, which forms a directly adjacent to the inner end of the torus 28 and provided for a boundary of the Torusinneren 28 wall portion 30.
- an extension 32 of the outer turbine closes nenschale 26 at. This extension 32 has a straight or annular shaped section 34.
- This straight or annular shaped portion 34 of the extension 32 may, for example, be such that it is substantially straight in the radial direction of the axis of rotation 36 of the torsional vibration damper 10 and, in particular as an annular portion, lies in a plane perpendicular to the axis of rotation 36 This spans.
- the torsional vibration damper 10 has a first energy storage device 38 and a second energy storage device 40.
- the first energy storage device 38 and / or the second energy storage device 40 are in particular spring devices.
- the first energy storage device 38 has a first energy store 42, such as spiral springs or bow springs, arranged in a circumferential direction extending around the axis of rotation 36, in particular at a distance from one another. It can be provided that all the first energy storages 42 are designed identically. It can also be provided that differently designed first energy store 42 are provided.
- the second energy storage device 40 has a plurality of, for example, each designed as a spiral spring or straight (pressure) spring, second energy storage 44.
- a plurality of second energy storage 44 circumferentially - with respect to the circumferential direction of the rotation axis 36 - spaced from one another. It can be provided that the second energy storage 44 are each designed identically; different second energy storage 44 can also be designed differently.
- the second energy storage device 40-with respect to the radial direction of the axis of rotation 36 - is arranged radially within the first energy storage device 38.
- the first 38 and the second energy storage device 40 are connected in series.
- the torsional vibration damper 10 has a first component 46, which is arranged between the first 38 and the second energy storage device 40 or connected in series with these energy storage devices 38, 40. It is therefore provided in particular that - for example, with the converter lock-up clutch 14 closed - a torque from the first energy storage device 38 via the first component 46 to the second energy storage device 40 is transferable;
- the first component 46 may also be referred to as an intermediate part 46, which will also be done below.
- the outer turbine shell 26 is connected to this intermediate part 46 such that a load, in particular torque and / or force, can be transmitted from the outer turbine shell 26 to the intermediate part 46 is.
- a driver part 50 is provided between the outer turbine shell 26 and the intermediate part 46 or in the load flow, in particular torque or force flow, between the outer turbine shell 26 and the intermediate part 46. It can also be provided that the extension 32 also forms the intermediate part 46 and / or the driver part 50, or assumes its function. It can also be provided that the driver part 50 forms a first component or intermediate part, which is connected in series in the torque flow between the energy storage devices 38, 40. It is further provided that along the load transfer path 48, via which a load or a torque from the outer turbine shell 26 is transferable to the intermediate part 46, at least one connecting means 52, 56 and 54, 58 is provided.
- connection means 52, 56 or 54, 58 may, for example, be a plug connection (see reference 58 in FIG. 4) or a riveted connection or bolt connection (see reference 56 in FIGS. 1 to 3 and 54 in FIG. or a welded joint (see reference numeral 52 in Figures 1 to 3) or the like. It should be noted that in Fig. 3 at the point where the welded joint 52 is given, in addition - to show an alternative design option - a rivet or bolt connection 54 is located. This should also clarify that the said connection means can also be designed differently or combined differently.
- connection means 52 designed as a welded connection (which, according to FIG. 3, can alternatively be a rivet or bolt connection)
- this driver part 50 rotatably coupled to the intermediate part 46 in each case via a connecting means 56 designed as a rivet or bolt connection.
- connection means 54 designed as a rivet or bolt connection
- this driver part 50 to the intermediate part 46 in each case via a connection means 58 designed as a plug connection rotatably coupled.
- all connection means 52, 54, 56, 58 by means of which along the load transfer path 48 between the outer turbine shell 26 and the intermediate part 46 adjacent components (such as extension 32 and driver part 50 and driver part 50 and intermediate part 46) are connected, are spaced from the immediately adjacent to the Torusinnere 28 wall portion 30 of the outer turbine shell 26. This allows - at least according to the embodiments - that the bandwidth of possible connecting means is increased.
- the second energy storage device 40 and the intermediate component 46 provided between these two energy storage devices 38, 40 are a second component 60 and a third component 62.
- the second component 60 forms an input part of the first energy storage device 38 and the third Component 62 forms an output part of the second energy storage device 40.
- a load or torque introduced from the second component 60 into the first energy storage device 38 can thus be transferred to the third component 62 via the intermediate part 46 and the second energy storage device 40 on the output side of this first energy storage device 38 ,
- the third member 62 engages a hub 64 to form a rotationally fixed connection, which in turn is rotatably coupled to an output shaft 66 of the torque converter device 1, which is, for example, a transmission input shaft of an automotive transmission.
- the outer turbine shell 26 is supported radially on the hub 64 by means of a support section 68.
- the support portion 68 which is supported in particular radially on the hub 64, is designed substantially sleeve-shaped. It should be noted that the addressed radial support of the outer turbine shell 26 by means of the support section 68 is such that supporting forces acting thereon on the outer turbine shell 26 are not conducted via the first or second energy storage device 38, 40 from the support section 68 to the outer turbine shell 26.
- the support portion 68 is rotatable relative to the hub 64. It may be provided that between the hub 64 and the support portion 68, a slide bearing or a plain bearing or a rolling bearing or the like is provided for the radial support. Furthermore, appropriate bearings may be provided for axial support.
- the above-mentioned connection between the outer turbine shell 26 and the intermediate part 46 is such that a torque transmittable from the outer turbine shell 26 to the intermediate part 46 can be transmitted from the outer turbine shell 26 to this intermediate part 46 without along the corresponding load transfer path 48th one of the energy storage devices 38, 40 is provided. This torque transmission from the outer turbine shell 26 to the intermediate part 46 (via the load transmission path 48) can thus be effected in particular by means of a substantially rigid connection.
- two connecting means are respectively provided along the load or force transmission path 48 between the outer turbine shell 26 and the intermediate part 46, namely a first connecting means 52 and 54 and a second connecting means 56 and 58.
- first connecting means 52 and 54 can be provided in the circumferential direction and / or preferably provided.
- simplification is also referred to as "the first connection means” or "the second connection means", which strictly speaking means one or more first connection means or one or more second connection means.
- the first connecting means 52 or 54 connects - in particular rotationally fixed - the extension 32 with the driver part 50 and the second connecting means 56 and 58 connects - in particular rotationally fixed - the driver part 50 with the intermediate part 46.
- the first connecting means 52 and 54 - with respect to the radial direction of the axis 36 - is arranged radially within the second connecting means 56 and 58, respectively.
- the first connection means 52 or 54 is arranged radially within the second energy storage device 40 or radially within the second energy storage 44 of the second energy storage device 40.
- the second connecting means 56 and 58 is there - with respect to the radial direction of the axis 36 - radially between the first energy storage device 38 and the second energy storage device 40 and the first energy storage 42 of the first energy storage device 38 and the second energy storage 44 of the second energy storage device 40 is arranged.
- the sleeve-like support region 68 is a radially inwardly located section of the driver part 50 with respect to the radial direction of the rotation axis 36
- a separate support part 70 is provided in the design according to FIG In any case, based on the radial direction of the axis of rotation 36 - radially inside the sleeve-like support portion 68 is formed.
- the support member 70 is there rotatably connected to the extension 32 and the driver part 50. This rotationally fixed connection also takes place here by means of the connection means 54, wherein it should be noted that separate connection means can also be provided.
- the converter lock-up clutch 14 is formed in the designs according to FIGS. 1 to 4 in each case as a multi-disc clutch and has a first disc carrier 72, of which first blades 74 are rotatably received, and a second disc carrier 76, of which second blades 78 are rotatably received.
- the first disk carrier 72 is relatively movable relative to the second disk carrier 76, in such a way that the first disk carrier 72 can be rotated relative to the second disk carrier 76.
- the second plate carrier 76 is here - with respect to the radial direction of the axis 36 - disposed radially within the first disc carrier 72, but this may be the other way round.
- the first plate carrier 72 is fixedly connected to the converter housing 16.
- the multi-plate clutch 14 on a piston 80 which is arranged axially displaceable and for actuating the multi-plate clutch 14 - for example, hydraulically - can be acted upon.
- the piston 80 is fixed or rotatably connected to the second plate carrier 76, which may be effected for example by means of a welded connection.
- First 74 and second blades 78 alternate - seen in the longitudinal direction of the axis of rotation 36 - from.
- this disk set 79 is supported on the side of the disk set 79 opposite the piston 80 at a portion of the inside of the converter housing 16.
- friction linings 81 are provided, which are held for example on the fins 74 and / or 78.
- the friction linings 81 which are provided on the end side of the disk set 79, can also be held on one side and / or on the other side on the inside of the converter housing 16 or on the piston 80.
- the piston 80 is formed integrally with the second component 60, that is to say the input part of the first energy storage device 38.
- the piston 80 is non-rotatably or fixedly connected to the second component 60 and the input part of the first energy storage device 38, wherein this fixed connection takes place here for example via a weld.
- this fixed connection takes place here for example via a weld.
- the rotationally fixed connection can also be done in other ways;
- the piston 80 and the input part 60 of the first energy storage device 38 may also be formed as a separate, fixed part or part fixed to one another, for example via a weld or a rivet or bolt be.
- FIG. 1 the piston 80 and the input part 60 of the first energy storage device 38 may also be formed as a separate, fixed part or part fixed to one another, for example via a weld or a rivet or bolt be.
- the piston 80 or the second component 60, the first component or the intermediate part 46, the third component 62 and the driver part 50 are each formed by sheets.
- the support part 70 can also be formed by a metal sheet.
- the second component 60 is in particular a flange.
- the first component 46 is in particular a flange.
- the third component 62 is in particular a flange.
- the mass moment of inertia of the driver part 50 is greater than the mass moment of inertia of the piston 80 or of the input part 60 of the first energy storage device 38 or the unit of these parts 60, 80.
- the Bleckdicke of the driver part 50 is greater than the Bleckdicke of the piston 80 and the input part 60 of the first energy storage device 38th
- the vibration behavior in the design according to FIG. 4 is worse than in the designs according to FIGS. 1 to 3.
- the vibration behavior of the device 1 is particularly good.
- a type of housing 82 is formed, which is at least partially, with respect to the radial direction and the axial direction of the axis of rotation 36. se on both sides axially and radially outside around the respective first energy storage 42 extends.
- this housing 82 is arranged on the driver part 50, whereas in the exemplary embodiment according to FIG. 4 it is arranged on the piston 80.
- the above-mentioned rotationally fixed arrangement on the driver part 50 or on the outer turbine shell is advantageous under aspects of vibration technology, since in this way more mass moment of inertia is shifted to the secondary side of the first energy storage device 38.
- the first energy stores 42 can each be supported on the addressed housing 82 for friction reduction via a rolling element, such as balls or rollers, having means 84, which can also be referred to as roller skate.
- rolling elements such as balls or rollers having means 84 for supporting the first energy storage 42 and for reducing friction in the designs according to FIGS. 1 and 2 and 4 may be provided in a corresponding manner.
- a sliding shell or a sliding shoe 94 is provided instead of such a roller skate 84 for the low-friction support of the first energy store 42.
- a second rotation angle limiting device 92 is provided for the second energy storage device 40, by means of which the maximum angle of rotation or relative rotation angle of the second energy storage device 40 or of the Input part of the second energy storage device 40 relative to the output part of the second energy storage device 40 is limited.
- the maximum angle of rotation of the second energy storage device 40 is limited by means of this second Verduswinkelbegrenzungs adopted 92 such that prevents the second energy storage 44, which are in particular springs, go at a correspondingly high torque load on block.
- the second Verduswinkelbegrenzungs Rhein 92 is - as shown in FIGS.
- the angle of rotation of the first energy storage device 38 is limited to a maximum first angle of rotation and the angle of rotation of the second energy storage device 40 is limited to a maximum second angle of rotation, wherein the first energy storage device 38 reaches its maximum first twist angle when a first limit torque is applied to the first energy storage device 38 and the second energy storage device 40 reaches its maximum second twist angle when a second limit torque is applied to this second energy storage device 40, this first limit torque being less than this second limit torque is.
- first energy store 42 at the first limit torque go to block, so that the first energy storage device 38 reaches its maximum first twist angle, and is effected by means of a second VerFDwin- kelbegrenzungs adopted for the second energy storage device 40 that the second energy storage device 40 at a second Limit torque reaches its maximum second angle of rotation, this maximum second angle of rotation is achieved when the second VerFDwinkelbegrenzungs adopted reaches a stop position.
- the angle of rotation of the first energy storage device 38 and the second energy storage device 40 - and the same applies to the maximum first and maximum second twist angle - is strictly speaking the relative twist angle with respect to the circumferential direction of the axis of rotation 36 of the torsional vibration damper 10 which is given in relation to the unloaded rest position between the input side and the output side for torque transmission respectively directly to the relevant energy storage device 38 or 40 adjacent components.
- This angle of rotation which is limited by the respective maximum first or second angle of rotation, in particular in the manner mentioned above, can change in particular in that the energy stores 42 and 44 of the respective energy storage device 38 or 40 absorb energy or deliver stored energy.
- the piston 80 or the second component or the input part 60 of the first energy storage device 38 forms a plurality of circumferentially distributed tabs 86, each having a non-free end 88 and a free end 90 , and which are provided for the front-side, input-side load of a respective first energy storage unit 42.
- the non-free end 88 is - with respect to the radial direction of the axis of rotation 36 - arranged radially within the free end 90 of the respective tab 86.
- the radial extent of the driver part 50 is greater than the average radial distance of the or the first energy store 42 from the second energy store or stores 44th
- hydrodynamic torque converter device Automotive powertrain torsional vibration damper transducer torque converter lockup clutch converter housing drive shaft, such as engine output shaft of an internal combustion engine pump or impeller stator turbine external turbine shell torus internal wall portion of 26 extension to 30 of 26 straight section of 32 or annular section of 32 rotation axis of 10 first energy storage device second energy storage device first energy storage second energy storage first component of load transfer path driver part or welding connection between 32 and 50 in 48 connecting means or bolt or rivet connection between 32 and 50 in 48 connecting means or bolt or rivet connection between 50 and 46 in 48 connecting means or connector between 50 and 46 in 48 second component third component hub output shaft, transmission input shaft support portion Supporting member first rack of 14 first slat of 14 second rack of 14 slats of 14 slat pack of 14 pistons for the operation of 14 friction lining of 14 housing roller skate tab non-free end of 82 free end of 82 second Vermoswinkelbegrenzungs liked 92 of 40 Gleitschuh
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hybrid Electric Vehicles (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/084,840 US8020680B2 (en) | 2005-11-10 | 2006-10-16 | Hydrodynamic torque converter device for an automotive drive train |
DE112006002800.6T DE112006002800B4 (de) | 2005-11-10 | 2006-10-16 | Hydrodynamische Drehmomentwandler-Vorrichtung für einen Kraftfahrzeug- Antriebsstrang |
JP2008539227A JP2009515116A (ja) | 2005-11-10 | 2006-10-16 | 自動車パワートレーンのためのハイドロダイナミック式のトルクコンバータ装置 |
EP06828489A EP1948976A1 (de) | 2005-11-10 | 2006-10-16 | Hydrodynamische drehmomentwandler-vorrichtung für einen kraftfahrzeug- antriebsstrang |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005053611.5 | 2005-11-10 | ||
DE102005053611 | 2005-11-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007054053A1 true WO2007054053A1 (de) | 2007-05-18 |
Family
ID=37770831
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2006/001820 WO2007054053A1 (de) | 2005-11-10 | 2006-10-16 | Hydrodynamische drehmomentwandler-vorrichtung für einen kraftfahrzeug- antriebsstrang |
Country Status (7)
Country | Link |
---|---|
US (1) | US8020680B2 (de) |
EP (1) | EP1948976A1 (de) |
JP (1) | JP2009515116A (de) |
KR (1) | KR20080066027A (de) |
CN (1) | CN101305216A (de) |
DE (1) | DE112006002800B4 (de) |
WO (1) | WO2007054053A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112149241A (zh) * | 2020-08-25 | 2020-12-29 | 东风汽车集团有限公司 | Tvd螺栓选型方法及tvd螺栓的拧紧参数的确定方法 |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8087508B2 (en) * | 2006-04-19 | 2012-01-03 | Volvo Lastvagnar Ab | Torsional vibration damper hub for a vehicle clutch |
DE102008057104B4 (de) * | 2007-11-22 | 2018-10-31 | Schaeffler Technologies AG & Co. KG | Kraftübertragungsvorrichtung und Verfahren zur Montage einer Dämpferanordnung in einer Kraftübertragungsvorrichtung |
US8727086B2 (en) * | 2010-12-22 | 2014-05-20 | Schaeffler Technologies Gmbh & Co. Kg | Three-stage hysteresis for series damper |
DE112012000708B4 (de) * | 2011-03-31 | 2017-08-03 | Aisin Aw Co., Ltd. | Starteinrichtung |
DE102012003385A1 (de) * | 2012-02-22 | 2013-08-22 | Man Truck & Bus Ag | Anordnung bestehend aus einem Verbrennungsmotor |
US20160252170A1 (en) * | 2014-12-09 | 2016-09-01 | Schaeffler Technologies AG & Co. KG | Torque converter drive connection |
US11731500B1 (en) * | 2022-07-29 | 2023-08-22 | Schaeffler Technologies AG & Co. KG | Drive plate assembly for hybrid module |
Citations (3)
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DE19514411A1 (de) * | 1994-04-26 | 1995-11-09 | Luk Lamellen & Kupplungsbau | Kraftübertragungseinrichtung mit Flüssigkeitskupplung |
DE19920542A1 (de) * | 1998-05-06 | 1999-11-18 | Luk Getriebe Systeme Gmbh | Kraftübertragungseinrichtung |
DE10358901A1 (de) * | 2003-04-05 | 2005-02-03 | Zf Sachs Ag | Torsionsschwingungsdämpfer |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4213341C2 (de) * | 1991-05-02 | 2003-09-25 | Luk Lamellen & Kupplungsbau | Hydrodynamische Einheit |
DE69621677T2 (de) * | 1995-03-17 | 2003-01-02 | Toyota Motor Co Ltd | Hydrodynamischer Drehmomentwandler mit Ueberbrückungskupplung und eingebautem Schwingungsdämpfer |
DE19724973C1 (de) * | 1997-06-13 | 1998-10-15 | Daimler Benz Ag | Anordnung einer 2-Wege-Torsionsdämpfereinheit und einer Kupplung in einem hydrodynamischen Drehmomentwandler |
FR2839128B1 (fr) * | 2002-04-30 | 2004-10-22 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
JP2004308904A (ja) * | 2003-04-05 | 2004-11-04 | Zf Sachs Ag | 捩り振動ダンパ |
-
2006
- 2006-10-16 KR KR1020087011136A patent/KR20080066027A/ko not_active Application Discontinuation
- 2006-10-16 EP EP06828489A patent/EP1948976A1/de not_active Withdrawn
- 2006-10-16 US US12/084,840 patent/US8020680B2/en active Active
- 2006-10-16 WO PCT/DE2006/001820 patent/WO2007054053A1/de active Application Filing
- 2006-10-16 CN CNA2006800421856A patent/CN101305216A/zh active Pending
- 2006-10-16 JP JP2008539227A patent/JP2009515116A/ja active Pending
- 2006-10-16 DE DE112006002800.6T patent/DE112006002800B4/de active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19514411A1 (de) * | 1994-04-26 | 1995-11-09 | Luk Lamellen & Kupplungsbau | Kraftübertragungseinrichtung mit Flüssigkeitskupplung |
DE19920542A1 (de) * | 1998-05-06 | 1999-11-18 | Luk Getriebe Systeme Gmbh | Kraftübertragungseinrichtung |
DE10358901A1 (de) * | 2003-04-05 | 2005-02-03 | Zf Sachs Ag | Torsionsschwingungsdämpfer |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112149241A (zh) * | 2020-08-25 | 2020-12-29 | 东风汽车集团有限公司 | Tvd螺栓选型方法及tvd螺栓的拧紧参数的确定方法 |
CN112149241B (zh) * | 2020-08-25 | 2022-11-01 | 东风汽车集团有限公司 | Tvd螺栓选型方法及tvd螺栓的拧紧参数的确定方法 |
Also Published As
Publication number | Publication date |
---|---|
CN101305216A (zh) | 2008-11-12 |
EP1948976A1 (de) | 2008-07-30 |
JP2009515116A (ja) | 2009-04-09 |
DE112006002800A5 (de) | 2008-09-04 |
US20090120754A1 (en) | 2009-05-14 |
KR20080066027A (ko) | 2008-07-15 |
DE112006002800B4 (de) | 2019-07-11 |
US8020680B2 (en) | 2011-09-20 |
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