IIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIII
`US008573374B2
`
`&12~ United States Patent
`et al.
`Magerkurth
`
`(Io) Patent No. :
`(45) Date of Patent:
`
`US 8,573,374 B2
`Nov. 5, 2013
`
`(54) HYDRODYNAMIC TORQUE CONVERTER
`
`(75)
`
`Inventors: Heiko Magerkurth,
`Freiburg im
`Breisgau (DE); Christian Huegel,
`Rheinau (DE); Andreas Meissner,
`(DE)
`Karlsruhe
`
`(73) Assignee:
`
`Schaeffler Technologies AG & Co. KG,
`HlezoOgenauraC (DE)
`
`( * ) Notice:
`
`the term of this
`Subject to any disclaimer,
`is extended or adjusted under 35
`patent
`U.S.C. 154(b) by 308 days.
`
`(21) Appl. No. :
`
`13/000, 076
`
`(22) PCT Filed:
`
`Jun. 12, 2009
`
`(86) PCT No. :
`) 371 (c)(I),
`(2), (4) Date:
`
`PCT/DE2009/000819
`
`Dec. 20, 2010
`
`(87) PCT Pub. No. : WO2010/000220
`PCT Pub. Date: Jan. 7, 2010
`
`(65)
`
`(30)
`
`Prior Publication Data
`May 5, 2011
`US 2011/0099992 Al
`
`Foreign Application Priority Data
`
`JUI. 4, 2008
`Aug. 14, 2008
`
`(DE)
`(DE)
`
`10 2008 031 431
`10 2008 037 808
`
`(51)
`
`Int. Cl.
`F16H 45/02
`(52) U.S. Cl.
`USPC
`
`(2006.01)
`
`... 192/3.29; 192/55. 61; 192/70. 17;
`192/30 V; 192/213. 1
`
`(58) Field of Classiiflication Search
`USPC ........................ 192/3.28, 3.29, 213.1; 60/338
`See application file for complete search history.
`
`(56)
`
`References Cited
`
`U.S. PATENT DOCUMENTS
`
`4,844,216 A
`6,026,940 A
`8, 161,740 B2 *
`2004/0226794 Al *
`2007/0181395 Al *
`2009/0125202 Al *
`
`7/1989 Fukushima
`.....
`2/2000
`Sudau
`.............
`4/2012 Krause et al.
`...
`11/2004 Sasse et al.
`8/2007 Mueller et al.
`Swank et al.
`5/2009
`
`..
`
`192/3. 26
`192/3. 28
`..... 60/338
`192/3. 29
`192/3. 29
`..... 701/68
`
`FOREIGN PATENT DOCUMENTS
`
`19804227
`DE
`10358901
`DE
`102006028556
`DE
`102008057648
`DE
`2009067988
`WO
`* cited by examiner
`
`8/1999
`2/2005
`1/2007
`6/2009
`6/2009
`
`Richard M. Lorence
`Primary Examiner
`Simpson& Simpson, PLLC
`(74) Attorney, Agent, orFirm
`
`ABSTRACT
`(57)
`The invention
`to a hydrodynamic
`relates
`converter
`torque
`having an impeller wheel, a turbine wheel and an oscillation
`damper which is accommodated in the converter housing, and
`lockup clutch. Two damper
`a converter
`stages are arranged
`here as a serial damper between the output hub of the torque
`lockup clutch, and a damper stage
`converter and the converter
`is arranged between the turbine wheel and the output hub. In
`a rotary oscillation
`order to improve the damping properties,
`absorber
`provided which is arranged between
`is additionally
`and is also connected to the turbine wheel
`in a
`the dampers
`fixed fashion.
`rotationally
`
`16 Claims, 1 Drawing Sheet
`
`7
`39
`
`33 40
`
`46
`23 22~
`45-
`13
`24—
`19—-
`43
`16-
`
`41
`7
`
`.¹2
`47
`-25
`3
`-33
`
`Valeo Exhibit 1001, pg. 1
`
`

`
`U.S. Patent
`U.S. Patent
`
`Nov. 5, 2013
`Nov. 5, 2013
`
`US 8,573,374 B2
`US 8,573,374 B2
`
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`Valeo Exhibit 1001, pg. 2
`
`Valeo Exhibit 1001, pg. 2
`
`

`
`US 8,573,374 B2
`
`1
`HYDRODYNAMIC TORQUE CONVERTER
`
`CROSS-REFERENCE TO RELATED
`APPLICATIONS
`
`This application is the National Stage of PCT International
`filed Jun. 12, 2009,
`Application No. PCT/DE2009/000819,
`which application published in German and is hereby incor-
`porated by reference in its entirety, which application claims
`priority from German Patent Application No. DE 102008 031
`431.5, filed Jul. 4, 2008 and from German Patent Application
`No. DE 10 2008 037 808.9, filed Aug. 14, 2008 which appli-
`cations are incorporated by reference in their entirety.
`
`FIELD OF THE INVENTION
`
`The invention relates to a hydrodynamic
`with a lock-up clutch and a multistage
`damper.
`
`torque converter
`torsional vibration
`
`BACKGROUND OF THE INVENTION
`
`Such torque
`used in vehicle
`are particularly
`converters
`trains, between
`combustion
`and
`an internal
`drive
`engine
`vibrations of an internal
`transmission.
`To damp torsional
`the so-called torsional vibration dampers
`combustion engine,
`are used, which are driven via an input part, whereby
`the
`to an output part
`is relatively and
`torque is transmitted
`that
`to said part, and through
`rotatable with respect
`limitedly
`compression of energy accumulators,
`the energy is tempo-
`rarily stored at torque peaks and released to the output part at
`torque troughs. The torque converter
`is configured by means
`of a damping
`a so-called
`device,
`conventional
`damper
`between the lock-up clutch and the output hub of the torque
`so that when the lock-up clutch is closed, torsional
`converter
`are damped via the torque path between converter
`vibrations
`the so-called turbine
`housing and output hub. Furthermore,
`dampers are known which by open or missing lock-up clutch,
`after initial hydraulic damping between impeller and turbine,
`still damp the remaining torsional vibrations
`and as such are
`disposed between the turbine
`and output hub. Furthermore,
`combinations of both damper
`types are known.
`form of reducing
`Another
`torsional
`the
`vibrations
`is
`absorber principle by which movable masses are disposed on
`the effect of energy accumula-
`mounting parts to counteract
`tors or in the case of centrifugal
`force pendulums,
`absorber
`in cir-
`masses are disposed tiltably on raceways
`extending
`cumferential-
`and radially direction and hence the inertial
`moment ofthe mounting part is varied depending on vibration
`influences.
`assembly space specifications
`Just as more restrictive
`in
`motor vehicles, especially in transverse drive units compris-
`combustion engine and transmission
`as well as
`ing internal
`the torque converter disposed in between, also the assembly
`for the embodiment of torque converters
`space requirement
`increases if sufficient vibration damping is sought. Task ofthe
`invention is therefore further development of a torque con-
`vibration
`verter with little assembly
`space but
`sufficient
`danlplng.
`
`BRIEF SUMMARY OF THE INVENTION
`
`The task is solved by means of a hydrodynamic
`torque
`converter with a turbine
`as well as
`driven by an impeller
`housing in which a torsional vibration damper with multiple
`stages and a torsional vibration absorber and a lock-
`damper
`up clutch are additionally mounted, whereby
`two damper
`
`10
`
`20
`
`25
`
`30
`
`35
`
`40
`
`45
`
`50
`
`55
`
`60
`
`65
`
`stages are disposed in series between the lock-up clutch and
`the torsional vibration absorber between the
`an output hub,
`stage between the turbine and
`stages, and a damper
`damper
`is con-
`output hub, whereby the torsional vibration absorber
`nected non-rotatably with the turbine. Through the proposed
`for instance a cen-
`a torsional vibration absorber,
`disposition,
`force pendulum,
`can be provided with both damper
`trifugal
`stages, so that the damper stages in overall can be designed for
`a smaller assembly space. A further advantage is the partition
`of the torsional vibration
`in at least
`two damper
`dampers
`stages, whereby the torsional vibration damper exercises two
`functions, namely that of a series damper and the other of a
`turbine damper. Through integration of both damper stages in
`features a torsional vibra-
`a single damper
`that concurrently
`stages, multiple com-
`tion absorber assigned to both damper
`ponents can be shared, so that in overall, for a given assembly
`capacity, a lighter and narrower
`space and damping
`torque
`converter can be proposed. For torque increase, particularly at
`a low speed range, a stator with one way clutch can be dis-
`fixed in housing
`posed moreover
`between
`non-rotatably
`impeller and turbine.
`The common inventive concept comprises a multiple num-
`ber of additional measures
`that can be combined or used
`in order to obtain a narrower assembly space. For
`individually
`instance, an input part of the first damper
`stage and an output
`part of the second damper
`stage can be centered on one
`so that, on the same axial assembly space, an input
`another,
`part and an output part can be mounted. Both components
`are
`to one another. For
`rotatably
`relative
`thereby
`supported
`instance, an output part of the second damper
`stage can be
`stage.
`disposed radially within the first damper
`of different
`components
`Furthermore,
`several
`damper
`function can be formed as one
`to their
`stages with respect
`piece. For instance, at least a disk part can be formed as one
`piece out of an in input- and an output part of two damper
`stages. For example, an output part of a radial, outer damper
`force support,
`stage can at the same time form a centrifugal
`in
`the disk part
`is guided accordingly radially outside, at
`that
`least partially around the energy accumulators. Window cut-
`can be provided
`outs for receiving the energy accumulators
`such a formed disk part can
`inside. Furthermore,
`radially
`hub or the turbine
`shell can at
`least be
`form the turbine
`mounted on said disk part, for instance riveted. This disk part
`can be mounted rotatably radially inside, on the output hub, so
`that with a flange part of the output hub by interposition of
`the
`direction,
`acting in circumferential
`energy accumulators
`stage can be formed as turbine damper.
`second damper
`The torsional vibration absorber
`is preferably formed as a
`force pendulum, whereby a mounting part accom-
`centrifugal
`modating absorber masses distributed over the circumference
`of the torsional vibration absorber and a disk part of the input
`part of a damper stage can be formed as one piece. Thereby, a
`input part, for instance, of the second damper stage
`two-part
`can be formed of two axially spaced disk parts, whereby the
`entails the mounting part and the
`first disk part concurrently
`second disk part is formed as one piece with the output part of
`the first damper stage. The disk part not containing the mount-
`for linking the torsional
`is connected non-rotatably,
`ing part
`to the first damper
`vibration absorber
`stage, with the other
`disk part by means of fastening means like rivets.
`can be
`axial assembly
`To minimize
`space, components
`they are radially dis-
`in that
`disposed axially over-lapping,
`slit or
`a radial
`posed where the other component
`features
`design. For instance, absorber masses of the torsional vibra-
`tion absorber and energy accumulators of the first damper
`can be disposed at the
`stage disposed over the circumference
`radially and axially spaced from one another,
`same height
`
`Valeo Exhibit 1001, pg. 3
`
`

`
`US 8,573,374 B2
`
`whereby a middle mounting diameter of the energy accumu-
`In this manner,
`lators is disposed radially outside the turbine.
`can at least partially axially overlap
`the energy accumulators
`for instance, on its torus tapering on the external
`the turbine,
`circumference.
`can be distributed
`the energy accumulators
`Furthermore,
`over the circumference of the second damper
`stage, based on
`a middle mounting
`the turbine
`diameter,
`radially within
`blades. The energy accumulators of the second damper stage
`can thereby particularly through the torus form ofthe turbines
`so close to the turbine
`be brought
`shell so that radial outer
`areas of the turbines
`and the axial edge areas of the energy
`intersect
`torsional
`accumulators
`the
`axially. Altogether,
`vibration damper can therefore be brought close to the tur-
`bine, so that the end of the torsional vibration damper
`towards
`the lock-up clutch is essentially flat and the lock-up clutch can
`be closer to the torsional vibration damper.
`reduction ofthe axial assembly space, the lock-
`For further
`up clutch in closed state can be disposed axially in a fastening
`means provided radially within the outside part of the torque
`converter mounted in a pocket formed on the housing wall. In
`the torque converter can be disposed closely on
`this manner,
`a flex plate or a drive plate, whereby
`a radially disposed
`constriction, about the rotation axis, of the converter housing
`can provide axial assembly space for the crankshaft with a
`for the flex plate.
`mounting
`can be disposed radially
`The lock-up clutch furthermore
`within the absorber masses. To increase the capacity of the
`torque capable of being transmitted
`by such reduced friction
`the lock-up clutch can be equipped with a friction
`diameter,
`plate that is pressurized by a piston centered on the output hub
`and that is axially displaceable on the housing and non-rotat-
`form-
`ably mounted axially opposite the converter housing
`ing a frictional closure.
`part for absorber masses can be disposed
`The mounting
`axially between the lock-up clutch and the first damper stage.
`For the transmission of torque from the lock-up clutch to the
`connections
`are
`transition
`stage
`first
`provided
`damper
`between the lock-up clutch and the input part of the first
`stage, which are guided through the mounting
`part.
`damper
`To allow rotational clearance between the fixed mounting part
`on output side and the input part of the first damper stage, the
`openings are provided in the mount-
`circular segment-shaped
`the passage openings
`ing part. Moreover,
`serve as limit stops
`and when rotary clearance is used up,
`they transmit
`torque
`to the first damper
`stage and directly via transmission
`further
`into the second damper
`connections
`stage.
`
`BRIEF DESCRIPTION OF THE SEVERAL
`VIEWS OF THE DRAWING
`
`The invention is illustrated in detail based on the exemplary
`in the only FIGURE. This FIGURE
`embodiment
`shown
`shows a hydrodynamic
`converter disposed about a
`torque
`rotation axis in a half-sectional
`view.
`torque converter 1
`The FIGURE shows the hydrodynamic
`in half-sectional view above the rotation axis 2. The housing
`3 is formed out of the housing parts 4, 5, which are welded
`of internal
`parts. The
`after
`with one another
`installation
`impeller 6 is integrated inside the housing part 4, so that upon
`rotation of the housing 3 the turbine 7 with turbine blades S is
`fluid inside the housing 3. The housing 3
`driven by converter
`not depicted. For
`is driven by an internal combustion engine
`fastening means 9 attached to the housing part 5,
`this purpose,
`for instance welded with a rigid drive- or flex plate preferably
`direction, are rig-
`axially elastic but rigid in circumferential
`idly connected with the crankshaft of the internal combustion
`
`engine, with the housing 3 after joining the torque converter
`e.g.
`connected
`on the transmission
`mounted
`and rigidly
`combustion engine. A stator 10 is
`screwed with the internal
`connected e.g. splined between an impeller 6 and turbine 7 via
`one-way clutch 11 with a transmission
`not depicted.
`stub
`The output part of the torque converter 1 is formed by the
`output hub 12, which is connected e.g. splined non-rotatably
`not depicted. A lock-up
`with a transmission
`shaft
`input
`clutch 13 is mounted inside the housing 3, which in the closed
`combustion
`from the internal
`state transmits
`the torque
`stages 14, 15 into the
`engine to the housing 3 via the damper
`output hub 12. When the lock-up clutch 13 is open,
`torque
`flows via the impeller 6 to the turbine and from there via the
`damper stage 15 into the output hub 12.For a slipping lockup
`clutch 13 partial
`torque can be transmitted
`via both torque
`paths.
`The lock-up clutch 13 is formed by a piston 1S rotatably
`hub 12, axially displaceable
`on the output
`mounted
`and
`sealed, which is connected non-rotatably with the housing by
`means of leaf springs 19.By adjusting a differential pressure
`between the two chambers 20, 21, piston 1S adjusts an axial
`force between itself and a housing wall 23, so that a frictional
`lock forms on the interposed friction plate 22 and the friction
`surfaces of the piston 1S and housing wall 23. The housing
`wall 23 is formed as an annular pocket 24 in which the piston
`1S and the friction plate 22 are fully received axially when the
`lock-up clutch 13 is closed. Through formation ofthe lock-up
`clutch 13 with a two-sided friction plate,
`the latter can for the
`same torque capable of being transmitted
`be mounted on a
`diameter
`that radially lies within the fastening means 9, so
`to the assembly space of the
`that an accommodation
`neutral
`lock-up clutch 13 is necessary with respect ofthe axial assem-
`bly. The fastening means 9 can therefore be displaced axially
`for a specified radial
`diameter
`the transmission
`towards
`through tapering of the housing part 5, so that the connection
`to the flex plate can occur by reducing an axial distance apart.
`The torsional vibration damper 16 with the damper
`stages
`14, 15 is designed
`damper. The two
`as a multi-function
`stages 14, 15 are connected with one another by a
`damper
`single-piece disk part 25 assigned to the damper stages 14, 15,
`which is centered rotatably radially inside on the output hub
`shell of the turbine 7
`12. Radially outside
`is the turbine
`connected with the disk part 25 by fastening means 26 e.g.
`rivets. Radially outside the fastening means 26, for instance,
`the energy accumulators 27, of the damper
`stage 15, formed
`as coil
`are
`circumference,
`over
`the
`distributed
`springs
`recesses 2S, which support
`the
`mounted in window-shaped
`energy accumulators
`formed-parts
`through correspondingly
`force effect. On the external circum-
`the centrifugal
`against
`ference of the disk part 25 are energy accumulators 29 of the
`stage 14 mounted and supported against centrifugal
`damper
`force. For this,
`the disk part 25 features
`30,
`formed-parts
`which surround the energy accumulators 29 radially. The disk
`the complete output part 34 of the
`part 25 thereby forms
`damper stage 14, whereas the disk part 25 in the damper stage
`15 forms a part of the input parts 35, which is completed by a
`second disk part 31 with corresponding
`window-shaped
`recesses 32. The two disk parts 25, 31 are axially spaced
`relative to one another by means of the rivets 33 and rigidly
`the flange part 36, which is
`connected and accommodate
`rigidly connected e.g. welded or formed as one piece with the
`output hub 12.To ensure the rotating ability ofthe flange part
`36, acting as output part 4S ofboth damper stages 14, 15, with
`to the input part 35 of the damper
`stage 15, circular
`respect
`shaped cutouts 49 are provided in the flange part 36,
`segment
`of the rotational
`clearance the
`after consumption
`whereby
`rivets 33 strike on the cutouts and the torque from the output
`
`5
`
`10
`
`15
`
`20
`
`25
`
`30
`
`35
`
`40
`
`45
`
`50
`
`55
`
`60
`
`65
`
`Valeo Exhibit 1001, pg. 4
`
`

`
`US 8,573,374 B2
`
`part 34 ofthe damper stage 14 is transmitted to the flange part
`36 and from there to the output hub 12.
`the disk part 31 in a single-piece man-
`In radial extension,
`part 37 of the torsional vibration
`ner
`forms the mounting
`absorber 17, which,
`forms a centrifugal
`through this design,
`force pendulum 3S, in that on both sides of the mounting part
`37 absorber masses 39 spaced axially apart are distributed
`are connected with one
`the circumference, which
`over
`another by means of rivets 40 and are guided in circumferen-
`tial direction and in radially extending raceways
`not visible
`in detail. Between the rivets 40 and the raceways, a bearing
`such as plain or roller bearing can be provided. Through the
`connection of the mounting
`part 37 with the
`single-piece
`input part 35 of the damper stage 15 and the output part 34 of
`the damper stage 15 by means of the rivets 33 is the centri fu-
`force pendulum 3S assigned parallel
`to both damper
`gal
`stages.
`The input part 41 ofthe damper stage 14 is formed by a ring
`part 42, which is centered on a centering circumference 43 of
`connected by means of
`the flange part 36 and is permanently
`connections 44 like rivets with a ring gear 45,
`transmission
`teeth 46 of the
`which forms a tooth system with an external
`friction plate 22. During assembly of both housing parts 4, 5,
`the tooth system is formed between the friction plate preas-
`sembled in the housing part 5 and the ring gear 45 preas-
`sembled in the housing part 4.
`part 37 or disk parts 31 is
`the mounting
`To ensure that
`openings 47 are provided
`rotatable, circular segment-shaped
`connections 44
`in said part,
`through which the transmission
`are guided.
`reduction of the axial assembly
`For further
`space are
`energy accumulators 29 disposed radially outside the turbine
`7 and surround
`axially. The
`least partially
`said turbine
`at
`energy accumulators 27 are brought closer to the turbine 7 in
`the tapered area between turbine blades S and the fastening on
`the disk part 25. The carrier masses 39 are closely spaced
`axially to the energy accumulators 29 radially disposed out-
`side the lock-up clutch 13.
`The functioning manner of the torsional vibration damper
`16 is differentiated
`in the state with actuated and non-actuated
`lock-up clutch 13.If this is opened then the damper
`stage 14
`is out of operation because the input part 41 is essentially
`load. The torque flows from the turbine 7 into the
`without
`stage 15 via the input part 35 and the energy accu-
`damper
`mulators 27 into the output part 4S as flange part 36 and from
`there via the output hub 12 into the transmission
`input shaft.
`When lock-up clutch 13 is actuated,
`the torque is intro-
`duced via the frictional plate 22, the gearing and the trans-
`mission connections 44 in the input part 41.The input part 41
`29, which can be arc
`pressurizes
`the energy accumulators
`the torque after consuming
`the
`and said transmit
`springs,
`rotary clearance of the cutouts 49 by means of limit stopped
`rivets 33, the torque to the common output part 4S acting as
`flange part 36 and from there via the output hub 12 on the
`27 are
`shaft. The energy accumulators
`transmission
`input
`preferably designed with stiffness, such that the torque trans-
`mitted through said stiffness does not lead to consumption of
`the rotary clearance and torque peaks are damped through the
`elastic properties of the energy accumulators. Thereby,
`the
`force pendulum 3S is active in a particularly
`centrifugal
`so that in the elastic operating range of
`advantageous manner,
`stages 14, 15, they are additionally
`both damper
`active in
`vibration damping.
`
`LIST OF REFERENCE SYMBOLS
`
`1 hydrodynamic
`2 rotation axis
`
`torque converter
`
`3 housing
`4 housing part
`5 housing part
`6 impeller
`7 turbine
`S turbine blade
`9 fastening means
`10 stator
`11 one way clutch
`12 output hub
`13 lock-up clutch
`14 damper
`stage
`15 damper
`stage
`16 torsional vibration damper
`17 torsional vibration absorber
`1S piston
`19 leaf spring
`20 chamber
`21 chamber
`22 friction plate
`23 housing wall
`24 pocket
`25 disk part
`26 fastening means
`27 energy accumulator
`2S recess
`29 energy accumulator
`30 formed-part
`31 disk part
`32 recess
`33 rivet
`34 output part
`35 input part
`36 flange part
`37 mounting
`part
`3S centrifugal
`force pendulum
`39 absorber mass
`40 rivet
`41 input part
`42 ring part
`43 centering circumference
`44 transmission
`connection
`45 ring gear
`46 external
`47 opening
`4S output part
`49 cutout
`is claimed is:
`What
`1.A hydrodynamic
`torque converter (1) with a turbine (7)
`(6) as well as housing (3) in which a
`driven by an impeller
`(16) with multiple of damper
`torsional
`vibration
`damper
`(17) and a
`(14, 15), a torsional vibration
`absorber
`stages
`lock-up clutch (13) are additionally
`installed, wherein a first
`stage (15) are dis-
`stage (14) and a second damper
`damper
`posed between the lock-up clutch (13)and an output hub (12),
`the second damper stage (15) is disposed between the turbine
`(12) and the torsional
`(7) and the output
`vibration
`hub
`stages (14, 15).
`absorber (17) is parallel
`to both damper
`2. The hydrodynamic
`(1) according to
`torque converter
`claim 1, wherein an input part (41) of the first damper
`stage
`(14) and an output part (4S) of the second damper
`stage (15)
`are centered on one another.
`3. The hydrodynamic
`(1) according to
`torque converter
`claim 1, wherein a disk part (25) is allocated to two damper
`stages (14, 15) as one piece.
`4. The hydrodynamic
`(1) according to
`torque converter
`(17) com-
`claim 1, wherein the torsional vibration absorber
`
`teeth
`
`6
`
`10
`
`16
`
`20
`
`26
`
`30
`
`36
`
`40
`
`46
`
`60
`
`66
`
`60
`
`66
`
`Valeo Exhibit 1001, pg. 5
`
`

`
`US 8,573,374 B2
`
`prises a plurality ofabsorber masses (39), and a mounting part
`(37) of the torsional vibration absorber (17) forms a disk part
`(31) of an input part (35) of the second damper
`stage (15).
`5. The hydrodynamic
`(1) according to
`torque converter
`claim 1, wherein absorber masses (39) of the torsional vibra-
`(29) of the first
`(17) and energy accumulators
`tion absorber
`are radi-
`stage (14) disposed over the circumference
`damper
`ally at the same height but axially spaced apart.
`6. The hydrodynamic
`(1) according to
`torque converter
`diameter of the energy
`claim 5, wherein a middle mounting
`(29) is disposed radially outside the turbine (7).
`accumulators
`7. The hydrodynamic
`(1) according to
`torque converter
`claim 5, wherein the energy accumulators
`(29) overlap the
`turbine (7) at least partially and axially.
`S. The hydrodynamic
`(1) according to
`torque converter
`claim 1, wherein energy accumulators
`(27) are distributed
`over the circumference ofthe second damper stage (15)based
`on a middle mounting diameter
`radially within turbine blades
`(S) of the turbine (7).
`9. The hydrodynamic
`(1) according to
`torque converter
`(27) of the second
`claim S, wherein the energy accumulators
`stage (15) and the turbine
`(7) at least partially and
`damper
`axially overlap.
`10. The hydrodynamic
`(1) according to
`torque converter
`claim 1, wherein the lock-up clutch (13) in a closed state is
`axially mounted in a pocket (24) formed in a housing wall
`(23) radially inward of fastening means (9)provided on exter-
`nal part of the torque converter (1).
`
`11.The hydrodynamic
`(1) according to
`torque converter
`claim 10, wherein the lock-up clutch (13) is formed out of a
`piston (1S) centered on the output hub (12) and mounted
`and axially displacably on the housing (3), and
`non-rotatably
`a friction plate (22) that can be clamped
`axially pressurizes
`between said piston and said housing (3) to develop a fric-
`tional engagement.
`12. The hydrodynamic
`(1) according to
`torque converter
`claim 11,wherein a mounting part (37) ofthe torsional vibra-
`tion absorber (17) is disposed axially between lock-up clutch
`stage (14).
`(13) and the first damper
`13. The hydrodynamic
`(1) according to
`torque converter
`claim 12, wherein between the friction plate (22) and an input
`part (41) of the first damper stage (14) transition connections
`(44) are formed, which reach through
`circular
`segment-
`(47) of the mounting part (37).
`shaped openings
`14.The hydrodynamic
`torque converter according to claim
`1, wherein in the closed state of the lock-up clutch (13) the
`(17) acts between both damper
`torsional vibration absorber
`stages (14, 15).
`15.The hydrodynamic
`torque converter according to claim
`1, wherein the torsional vibration absorber (17) is connected
`non-rotatably with the turbine (7).
`16.The hydrodynamic
`torque converter according to claim
`15, wherein in the opened state of the lock-up clutch (13)the
`torsional vibration absorber (17) is connected non-rotatably
`with the turbine (7).
`
`5
`
`10
`
`15
`
`20
`
`25
`
`Valeo Exhibit 1001, pg. 6