(12)UK Patent Application l19lGB (11)2 271 411 l13lA
`
`(43) Date ofA Publication 13.04.1994
`
`(21) Application No 93203123
`
`(22) Date of Filing 01.10.1993
`
`(30) Priority Data
`(31)
`4234304
`-
`
`(32) 12.10.1992
`
`(33) DE
`
`(71) ADD)“-‘3ntl5)
`l-"K Lamellen "Nd Kuwlunssbau Gmbfl
`
`(51)
`
`INT CL5
`F16D 3/12 . F16H 45/02
`
`(52) UK CL (Edition M)
`F2U U286 U288 U340
`F2W W1OB1 W10B2 W20X1
`U15 $2015
`
`(56) Documents Cited
`ca 2255395 A
`GB 2098702 A
`
`GB 2124334 A
`US 5020647 A
`
`GB 2123924 A
`
`(Incorporated in the Federal Republic of Germany)
`
`_
`Postfach 14 54, 77813 Buhl,
`Federal Republic of Germany
`
`(58)
`
`Field of Search
`UK CL (Edition L) FZU
`INT CL5 F1 5H
`
`(72)
`
`lnventorls)
`Roland Seebacher
`Helmut Muller
`Dieter Otto
`Steven Olsen
`
`(74) Agent and/or Address for Service
`Dummett copp & Co
`25 The Square, Martlesham Heath, IPSWICH, lP5 7SL,
`United Kingdom
`
`(54) Torque converter etc.with damper assembly
`
`(57) A power transfer device with a fluid clutch such as a torque converter has at least one rotationally elastic
`dampener mounted in the power flow between the housing and a driven part of the device. A housing 2
`formed by members 5, 6 is connected to a drive shaft such as the crankshaft of an engine and contains a pump
`wheel 10 and a turbine wheel 13 connected to a gearbox drive train. At least one rotationally elastic damper 16
`having at least one circumferentially acting energy accumulator 19 mounted in the radially outer area of, and
`in the power flow between, the turbine wheel and the driven part of the device.
`
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`At least one drawing originally filed was informal and the print reproduced here is taken from a later filed formal copy.
`
`Valeo Exhibit 1013, pg. 1
`
`Valeo Exhibit 1013, pg. 1
`
`

`
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`Valeo Exhibit 1013, pg. 2
`
`Valeo Exhibit 1013, pg. 2
`
`

`
`Valeo Exhibit 1013, pg. 3
`
`Valeo Exhibit 1013, pg. 3
`
`

`
`Valeo Exhibit 1013, pg. 4
`
`Valeo Exhibit 1013, pg. 4
`
`

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`Valeo Exhibit 1013, pg. 5
`
`Valeo Exhibit 1013, pg. 5
`
`

`
`-1-
`
`2271411
`
`POWER TRANSFER DEVICE
`
`The invention relates to a power transfer device with fluid
`
`such as a Ebttinger clutch, hydrodynamic torque
`clutch,
`converter or the like with at least one housing connectable
`
`with a drive shaft and containing at least one pump wheel
`
`least one turbine wheel
`driven by the housing and at
`connectable with the input shaft of a drive train such as a
`gearbox, and where applicable containing at least one guide
`wheel mounted between the pump wheel and turbine wheel, with
`
`furthermore at
`
`least one rotationally elastic dampener
`
`mounted in the power flow between the housing and a driven
`part of the device and having at least one circumferentially
`acting energy accumulator. The invention also relates inter
`alia to those power
`transfer devices having a so-called
`
`bridging clutch.
`
`The object of the present invention is to improve devices of
`this kind, more particularly their dampening action wherein
`the possibility is to be provided of making large angular
`deflections between the input part and output part of the
`
`device. When using a converter bridging clutch it should
`
`furthermore be possible through the invention to transfer a
`
`high torque in relation to the closing pressure necessary
`for this purpose.
`Furthermore the device according to the
`invention should be
`capable of
`simple cost-effective
`
`More particularly low manufacturing and
`production.
`assembly costs should be possible through structural design
`measures.
`Furthermore the aim of
`the invention is to
`
`minimize the wear and increase the service life of
`
`the
`
`Power transfer devices which are
`complete assembly unit.
`fitted with a converter bridging clutch are generally
`
`designed so that the converter bridging clutch only closes
`at higher speeds,
`that is connects the input and output
`parts of
`the power
`transfer device.
`By closing the
`
`Valeo Exhibit 1013, pg. 6
`
`Valeo Exhibit 1013, pg. 6
`
`

`
`-2
`
`converter bridging clutch the engine torque is transferred
`by by-passing the hydraulic part of the torque converter and
`thus cuts out the losses which arise through the unavoidable
`
`slip in the converter. These slip losses in the converter
`appear in an increased energy consumption.
`A further aim
`of the invention is, for example in order to save energy, to
`
`keep the converter bridging clutch closed in the largest
`possible operating range and thereby to obtain the vibration
`comfort which is provided by the torque converter in the
`
`However to
`case of an opened converter bridging clutch.
`this end it is necessary to close the converter bridging
`clutch at a lower speed.
`In order to achieve the required
`
`comfort it is necessary to shift the inherent frequency of
`
`the actual vibration form of the part of the drive train
`
`which comprises the complete drive train parts from the
`
`gearbox inlet to the differential, into an area which is not
`
`contacted during normal driving operation.
`
`This is achieved according to the present invention in that
`
`the energy accumulator is mounted radially outside and in
`
`the power flow between at least one turbine wheel and the
`
`driven part of
`
`the device.
`
`By mounting the energy
`
`accumulator radially outside it.becomes possible to store up
`
`the maximum amount of spring capacity or spring volume.
`
`With the simultaneous comparatively lower spring rate which
`
`lowers the resonance speed this allows very large turning
`
`angles or very large spring paths.
`
`It can be particularly advantageous with a device according
`
`to the invention if at
`
`least
`
`the energy accumulator is
`
`mounted axially between the turbine wheel and the housing
`wall on the side of the drive shaft.
`
`It can be expedient, for example regarding the effects on
`
`the resonance speeds,
`
`to design the power transfer device
`
`5P127l+.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 7
`
`Valeo Exhibit 1013, pg. 7
`
`

`
`_ 3 -
`
`according to the invention so that the spring rate of the
`rotationally elastic dampener amounts to between 5 and 20
`Nm/', preferably between 8 and 15 Nm/'.
`
`Furthermore it can prove advantageous if the individual
`energy accumulators of the rotationally elastic dampener -
`viewed over the circumference of the device - extend over an
`
`It can be
`angle in the order of between 75 and 175'.
`particularly expedient for the construction if the energy
`accumulators are pre—curved at least approximately to that
`
`diameter on which they are mounted.
`
`There can be a positive effect on the service life of a
`power transfer device according to the invention if the
`energy accumulators are supported at least radially outside
`at least partially on a wear—protection member.
`It can be
`expedient if the wear protection member is formed by at
`
`least one separately inserted part.
`
`It can be particularly advantageous if parts supporting
`biasing areas for the energy accumulators mounted radially
`on the outside at least partially surround same radially
`
`outwards and are connected rotationally’ secured to the
`
`turbine wheel.
`
`It
`
`can thereby be expedient
`
`if the
`
`rotationally secured connection is made radially on the
`
`inside.
`
`In other cases it can however be advantageous
`
`if the
`
`rotationally secured connection is formed in the radially
`
`outer area of the turbine wheel.
`
`Quite generally it can be advantageous with a power transfer
`
`device according to the invention if the energy accumulators
`
`are supported on the other side on an output part of the
`
`dampener which is connected rotationally secured at least
`
`591274.93
`23 September 1993
`
`Valeo Exhibit 1013, pg. 8
`
`Valeo Exhibit 1013, pg. 8
`
`

`
`_ 4 _
`
`indirectly to the driven part of the power transfer device.
`
`It can thereby prove particularly expedient if the output
`
`part of the radially outer dampener forms the input part of
`
`a further radially inner dampener which is in turn supported
`
`on the other side on an output part which is connected
`
`rotationally secured to the driven shaft of
`
`the power
`
`transfer device .
`
`For an embodiment of a torque transfer device according to
`
`the invention it can be advantageous if the biasing areas
`
`for
`
`the
`
`energy accumulators
`
`are
`
`connected at
`
`least
`
`indirectly by a welded connection to the turbine wheel.
`
`Quite generally it can be expedient to connect a bridging
`
`clutch in series with the dampener.
`
`Furthermore it can prove advantageous if the output part of
`
`the bridging clutch is connected rotationally secured to the
`
`input part of the rotationally elastic dampener.
`
`It can
`
`thereby be expedient if the output part of the bridging
`
`clutch is axially displaceable.
`
`It can again be advantageous here if the output part of the
`
`bridging clutch is axially displaceable relative to the
`
`input part of the rotationally elastic dampener.
`
`It can prove particularly advantageous
`
`if the friction
`
`surface of the bridging clutch is mounted in the diameter
`
`range of the radially outer dampener.
`
`An advantageous design of a torque transfer device according
`
`to the invention can consist in mounting the output part of
`
`the bridging clutch axially between the housing wall on the
`
`side of
`
`the drive and the rotationally elastic dampener
`
`lying radially on the outside.
`
`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 9
`
`Valeo Exhibit 1013, pg. 9
`
`

`
`-5-
`
`It can prove particularly expedient if the output part of
`the bridging clutch is designed as a piston.
`It can thereby
`be advantageous if the output part of the bridging clutch is
`mounted axially and circumferentially movable but sealed on
`a component held by the driven shaft of the power transfer
`
`device.
`
`It can be expedient if the rotationally secured connection
`between the output part of the bridging clutch and the input
`part of the dampener is designed with keyed engagement.
`It
`can thereby be particularly advantageous
`if the keyed
`engagement is formed by teething at the ends of the parts to
`be connected.
`
`It can furthermore be expedient if in the case of a power
`
`transfer device this connection is produced by leaf springs.
`
`A further basic inventive idea relates to a power transfer
`
`device with fluid clutch with at
`
`least
`
`one housing
`
`connectable with the drive shaft and containing at least one
`
`pump wheel driven by the housing and at least one turbine
`wheel connectable with the input shaft of a drive train as
`
`well as if required containing at least one guide wheel
`
`between the pump and turbine wheels,
`
`furthermore with at
`
`least one rotationally elastic dampener mounted in the fore
`
`flow between the housing and a driven part of the device
`
`with
`
`at
`
`least
`
`one
`
`circumferentially
`
`active
`
`energy
`
`accumulator wherein the energy accumulator is mounted in the
`
`radially outer area between at least one turbine wheel and
`the driven part of the device wherein the biasing areas for
`the dampener are connected axially and rotationally secured
`to the turbine wheel and are mounted together with same
`
`axially displaceable and relatively rotatable at
`
`least
`
`indirectly on the driven part of the device.
`
`SP1274. P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 10
`
`Valeo Exhibit 1013, pg. 10
`
`

`
`With a power
`
`transfer device of
`
`this kind it can be
`
`advantageous
`
`if the turbine wheel
`
`is supported by an
`
`intermediate part with a hub mounted on the driven part.
`
`The
`
`intermediate part
`
`can
`
`thereby define the axial
`
`displacement of the turbine wheel in at least one direction.
`
`A favourable result is achieved - for example with regard to
`
`the manufacturing costs - if the intermediate part is made
`
`of plastics.
`
`It can be advantageous if the biasing areas for the dampener
`
`are connected to the turbine wheel by a part of L-shaped
`
`cross-section projecting axially over the biasing areas
`
`whereby a compact construction can be achieved.
`
`The
`
`connection is preferably designed as a welded connection.
`
`It can be particularly advantageous if the component having
`
`the L-shaped cross-section is the output part of a bridging
`
`clutch.
`
`It can then be expedient if the component having the L-
`
`shaped cross-section has friction linings or one friction
`
`lining.
`
`Furthermore the invention relates to a power transfer device
`
`with fluid clutch, such as a Fottinger clutch, hydrodynamic
`
`torque converter or the like with at
`
`least one housing
`
`connectable with a drive shaft and containing at least one
`
`pump wheel driven by the housing and at least one turbine
`
`wheel connectable with the input shaft of a drive train such
`
`as a gearbox, as well as if required containing at least one
`
`guide wheel between the pump wheel and turbine wheel, with
`
`furthermore at
`
`least
`
`two rotationally elastic dampeners
`
`mounted in the power flow between the housing and the driven
`
`part of
`
`the device with at
`
`least one circumferentially
`
`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 11
`
`Valeo Exhibit 1013, pg. 11
`
`

`
`-7-
`
`acting energy accumulator
`
`for each, wherein ‘the energy
`
`accumulator of one dampener is mounted in the power flow
`
`between the at least one turbine wheel and the driven part
`
`of
`
`the device and the energy accumulator of
`
`the other
`
`dampener is mounted in the power flow between the housing
`
`and at least one turbine wheel.
`
`It can thereby be advantageous if the energy accumulators of
`
`the other dampener are mounted radially on the outside but
`
`it can also be expedient
`
`to mount
`
`these radially on the
`
`inside.,
`
`It can prove particularly advantageous if with a power
`transfer device the at
`least one
`friction face of a
`
`converter bridging clutch is mounted radially between the
`
`energy accumulators of the one and other dampener.
`
`It can
`
`thereby be expedient
`
`if the output part of
`
`the other
`
`dampener is connected by the converter bridging clutch to
`
`the input part of the one dampener.
`
`In a preferred embodiment of a torque transfer device
`
`according to the invention the input part of one dampener is
`
`formed by the turbine wheel and the input part of the other
`
`dampener is formed by the housing wherein it is however
`possible to associate the different input parts with each
`
`other dampener.
`
`It can be advantageous
`
`if the output part of
`
`the one
`
`dampener is connected rotationally secured to the driven
`
`part of the device.
`
`Quite generally it can be expedient if the turbine wheel is
`
`centred by the driven part of the device.
`
`Furthermore it can be advantageous if a disc-like component
`
`SP‘l274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 12
`
`Valeo Exhibit 1013, pg. 12
`
`

`
`-3
`
`designed as a piston for the converter bridging clutch is
`
`centred by the driven part of the device.
`
`It can prove particularly advantageous if between the disc-
`
`like part designed as a piston, and the driven part of the
`
`device there is a centring sleeve which has at least one
`
`sealing area which interacts with the radially inner area of
`
`the disc-like component designed as a piston.
`
`An expedient embodiment of a power transfer device according
`
`to the invention can provide that the output part of the
`
`other
`
`dampener
`
`is held radially centred and axially
`
`displaceable on the output part of the one dampener.
`
`It can be particularly advantageous if the input part of the
`
`one dampener is connected rotationally secured to the disc-
`
`like component which acts as a piston.
`
`Advantageously the centring sleeve and
`
`the disc-like
`
`component designed as a piston are connected together
`
`secured against rotation.
`
`It can thereby be advantageous if the rotationally secured
`
`connection is subject to play.
`
`The
`
`invention will
`
`now" be explained with reference to
`
`Figures 1 to 4.
`
`In the drawings:
`
`Figure 1
`
`is a simplified sectional view through a device
`
`Figure 2
`
`according to the invention;
`is a simplified sectional view through another
`
`embodiment
`
`of
`
`a
`
`device
`
`according
`
`to
`
`the
`
`invention;
`
`is a partial view of a cross—section according to
`
`591274.93
`23 September 1993
`
`Valeo Exhibit 1013, pg. 13
`
`Valeo Exhibit 1013, pg. 13
`
`

`
`-9-
`
`arrows III of Figure 2 wherein for reasons of
`
`clarity individual parts have been removed;
`
`Figure 4
`
`simplified sectional View of a further
`is a
`embodiment.
`
`The device 1
`
`shown in Figure 1 has a housing 2 which
`
`contains a hydrodynamic torque converter 3.
`
`The housing 2
`
`is connected to a driving shaft which can be formed by the
`
`driven shaft such as eg crankshaft of an internal combustion
`
`engine. The rotationally secured connection can thereby be
`provided between the shaft and housing 2 by a drive plate
`(not
`shown
`in
`further detail) which
`is
`connected
`rotationally secured radially on the inside to the driving
`
`shaft and radially on the outside to the housing 2 for
`
`example by screws which engage in the fastening thread 4.
`
`The housing 2 is formed by a housing dish 5 adjoining the
`
`driving shaft, as well as by a further housing dish 6 fixed
`
`on the dish 5. The two housing dishes 5 and 6 are connected
`
`fixedly together
`
`radially on
`
`the outside by a
`
`screw
`
`connection 7 and are sealed by means of a sealing attachment
`
`8.
`
`one part of the sealing area 8 is formed by a ring
`
`flange like part 9 which in turn is fixedly connected to the
`
`housing dish 6.
`
`In the illustrated embodiment the housing
`
`dish 6 is drawn up directly in order to form the outer dish
`
`of
`
`the pump wheel 10.
`
`To this end the blades 11 are
`
`connected to the housing dish 6
`
`in known way.
`
`Axially
`
`between the pump wheel 10 and the radial wall 12 of the
`
`housing dish 5 there is a turbine wheel 13 which is mounted
`
`rotatable on a driven hub 14 which is coupled rotationally
`
`secured to an input shaft of a gearbox by internal teething.
`Axially between the inner areas of the pump 10 and turbine
`
`wheel 13 is a guide wheel 15.
`
`Furthermore in the inner space formed by the two housing
`
`SP1274 . P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 14
`
`Valeo Exhibit 1013, pg. 14
`
`

`
`-10-
`
`dishes 5 and 6 there is a rotationally elastic dampener 16
`
`which ensures a rotationally elastic coupling of the driven
`
`hub 14 with a driving part which in the illustrated
`
`embodiment is fixedly connected by screws 17 to the turbine
`
`wheel 13.
`
`AA converter bridging clutch is provided in series
`
`with the rotationally elastic dampener 16.
`
`The
`
`rotationally elastic dampener
`
`16
`
`comprises
`
`energy
`
`accumulators 19 which in the illustrated embodiment are each
`
`formed by two interengaging coil springs 20, 21. The energy
`
`accumulators 19 can thereby extend at least approximately
`
`over half the circumference of the device but as shown in
`
`particular in Figure 3 they can also each cover the largest
`
`part of a quarter circle. Depending on the type of use it
`
`is
`
`expedient
`
`if
`
`an
`
`energy
`
`accumulator
`
`19,
`
`viewed
`
`circumferentially, extends over an angle lying in the order
`
`of between 70 and 175 degrees. The individual coil springs
`
`20, 21 can thereby be pre-curved at least approximately to
`
`the radius
`
`apparent
`
`for
`
`example
`
`from Figure 3 which
`
`corresponds to the installation radius whereby the assembly
`
`of
`
`the device
`
`is made
`
`considerably easier
`
`since no
`
`additional means are required to obtain the curvature of the
`
`springs 20, 21. The energy accumulators 19 and coil springs
`
`20,
`
`21
`
`respectively are
`
`supported at
`
`least
`
`through
`
`centrifugal power on an area 22 axially engaging over the
`
`and connected to the disc-like
`19
`energy accumulators
`component 23 which forms at least partially the biasing
`
`areas for the energy accumulators 19. The component 23 is
`
`in the illustrated embodiment connected to the turbine wheel
`
`13 by fastening screws 17 wherein this assembly unit is
`
`mounted radially inwards rotatable on the driven hub 14.
`
`However in another type of bearing for the turbine wheel 13
`
`on the driven shaft 14 it is also possible to replace the
`
`disc-like component 23 by a circular ring shaped toroidal
`
`structure which can then be connected for example in the
`
`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 15
`
`Valeo Exhibit 1013, pg. 15
`
`

`
`-11-
`
`area 23a fixed to the turbine wheel 13 by means of welding
`
`or other type of connection.
`
`In order to reduce the wear additional support dishes (not
`
`shown in further detail here) can be provided between the
`
`axial area 22 and the windings of the outer coil springs 20.
`
`These support dishes can thereby extend over the length of
`the energy accumulators 19, as shown for example in Figure
`3 and are designed with curved cross-section so that they
`conform at least approximately to the outer contour of the
`
`windings of the coil springs 20 whereby the contact areas
`between the coil spring windings and the support dishes can
`be enlarged and thus the wear can be correspondingly reduced
`
`or even avoided altogether.
`
`the disc-like
`Radially inside the energy accumulators
`component 23 is connected axially and rotationally secured
`by spacers such as rivets 24 to a circular ring-shaped
`component 25. This circular ring-shaped component 25 forms
`in the diameter range of the energy accumulator 19 biasing
`areas for
`same which are mounted corresponding to the
`
`biasing areas of
`
`the disc-like component
`
`23 which are
`
`mounted there.
`
`The biasing areas in the components 23 and
`
`25 can be formed by axial deformations of the components
`
`relative to each other such as for example indented pockets.
`
`In other embodiments it may be expedient
`
`to form these
`
`biasing areas by additional components such as for example
`
`by welding on circular segment-like areas.
`
`ring shaped
`Radially inside the rivetting the circular
`component 25 has a connecting area 26 through which the said
`component
`is
`connected
`rotationally secured
`to the
`substantially disc-like piston 27 of the converter bridging
`
`clutch 18. The rotationally secured connection in the area
`
`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 16
`
`Valeo Exhibit 1013, pg. 16
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`

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`-12..
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`26 allows an axial displacement of the piston 27 relative to
`
`the turbine wheel 13 and the parts connected to same and is
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`designed here as end gearing. The rotationally secured but
`axially pliable or displaceable connection in the connecting
`area 26 can however also be made by other suitable means,
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`such as for example leaf springs.
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`The piston 27 of the
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`converter bridging clutch 18 is mounted, with its radially
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`inner area 28 extending axially away from the wall 12 of the
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`housing part 5 on the drive side, axially displaceable on
`the hub part 14 and rotatable relative thereto. The piston
`27 of the converter bridging clutch 18 and the hub 14 are
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`sealed relative to each other by means of the seal 29 and
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`can thus fornt a pressure-tight
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`space 30 which. extends
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`substantially radially outwards between the housing wall 12
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`and the side of the piston 27 facing same.
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`The radially
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`outer seal of the pressure-tight space 30 is formed - when
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`the converter bridging clutch 18 is closed - by the friction
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`areas 31 of the piston 27 and 32 of the housing wall 12 as
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`well as by the friction lining 33 which is applied to one of
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`the two friction areas 31,32.
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`The energy accumulators 19 or the coil springs 20, 21 are,
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`as can be seen from the drawings, mounted on the largest
`
`possible diameter so that a.maximum.of spring capacity, that
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`is the largest possible spring volume, can be stored up.
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`This allows very large spring paths or very large turning
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`angles with simultaneously relatively low spring rates. The
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`turning angles thus possible can be for example in the order
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`of between 40 and 75 degrees and the torsion rates which can
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`be achieved lie in the order of between 2 and 15 Nm/'. The
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`values given here are for when using a single rotationally
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`elastic dampener,
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`thus when using a single spring set
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`wherein the springs act together in parallel.
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`In many cases
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`it can be expedient to set the turning rigidity and thus the
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`turning rate of the rotary elastic dampener in the order of
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`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 17
`
`Valeo Exhibit 1013, pg. 17
`
`

`
`between 4 and 15 Nm/'.
`
`The output part of the rotationally elastic dampener 16 is
`formed by a flange-like or disc-like component 34 which has
`on its outer circumference,
`thus on its outer periphery
`
`radial
`
`extensions or
`
`arms
`
`35
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`for biasing the energy
`
`accumulators 19.
`
`In the rest state of the device 1 these
`
`extensions 35 are located in the axial direction between the
`pockets or
`the biasing areas which are formed in the
`components 23 and 25. As apparent for example in connection
`with
`Figure
`3,
`the
`energy
`accumulators,
`viewed
`circumferentially, can be made slightly shorter than the
`angular distance between two adjoining extensions 3 and 30
`so that, starting from the zero or rest position of the
`device, a certain turning is possible at first without the
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`energy accumulators becoming compressed.
`
`In its radially inner area the flange 34 is firmly connected
`to an axially extending flange-like section of the hub 14,
`
`for example by rivets 36. This rivetting can also be formed
`differently from the illustrated example, by drawing up
`material directly from the hub 14.
`Between the radially
`
`the hub 14 facing the
`extending axial boundary face of
`housing wall 12 and the side of the housing wall 12 facing
`the hub is a run-up disc 37. The run-up disc 37 defines the
`
`axial displacement of all the components connected to the
`hub 14 in the direction of the housing wall 112 and is
`
`The run-up disc 37 is
`substantially circular ring shaped.
`fixed in the circumferential direction on the hub 14 by
`
`axially extending areas 38 which are set up out of the run-
`up disc in the direction away from the housing wall 12.
`In
`order to ensure good sliding properties of the run-up disc
`37 relative to the parts standing in sliding connection with
`
`same the disc can be made for example from a coated sheet
`
`metal plate or a bronze plate. Furthermore it is possible
`
`sP1274. P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 18
`
`Valeo Exhibit 1013, pg. 18
`
`

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`to use a plastics part at this point.
`
`-14..
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`The bridging clutch 18 is closed by the pressure produced by
`
`the fluid such as oil contained in the interior of the
`
`housing 2 which (pressure) produces an axial force in the
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`direction of the housing wall 12 on the side of the piston
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`27 facing the turbine wheel 13.
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`In order to open the
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`bridging clutch 18 pressurised medium is supplied to the
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`ring space 30 through the supply channel 39 until the axial
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`force resulting therefrom reaches a sufficient level to move
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`the piston 27 axially in the direction of the turbine wheel
`13 and thus the friction areas 31 of the piston 27 and 32 of
`
`the housing wall 12 are lifted from each other. when the
`
`bridging clutch 18 is opened pressurised medium can flow
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`radially outwards
`
`from the ring space 30 between the
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`friction areas 31 of the piston 27 and 32 of the housing
`
`wall 12.
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`The unit 101 shown in Figures 2 and 3 is similar mainly in
`
`function but also in construction to the unit 1 described in
`
`connection with Figure 1, and parts which carry out the same
`
`or similar function as described in connection with Figure
`
`1 have similar reference numerals, but increased by 100.
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`In the power transfer unit 101 there is a turbine wheel 113
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`likewise mounted between the pump wheel 110 and the radial
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`wall 112 of the housing dish 105.
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`The turbine wheel is
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`mounted
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`rotatable
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`and
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`axially
`
`displaceable
`
`on
`
`an
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`intermediate part 140 which in turn is nmunted with the
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`addition of a seal 141 on the driven hub 114 which is
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`coupled rotationally secured to the gear input shaft by
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`internal gearing. The intermediate part 140 can thereby be
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`designed as a plastics part or can however also be made for
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`example of aluminium.
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`The inner space formed by the two
`
`housing dishes 105 and 106 in turn houses a rotationally
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`SP1274. P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. _19
`
`Valeo Exhibit 1013, pg. 19
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`

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`-15-
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`elastic dampener 116 which connects the driven hub 114 to a
`_ driving part, which here is welded to the turbine wheel 113
`in a radially outer area. Furthermore a converter bridging
`clutch 118 is provided in series with the rotationally
`
`elastic dampener 116.
`
`The energy accumulators 119 are supported at least through
`centrifugal force on the area 122 of the drive part 123
`engaging axially over same and having an approximately L-
`shaped cross—section.
`The turbine wheel 113 is fixedly
`connected in its radially outer area with the drive part 123
`
`by a welded seam 142.
`
`The friction area 131 of the converter bridging clutch 118
`
`is mounted on the free radially inwardly pointing arm 143 of
`the L-shaped drive part 123 which directly adjoins the
`housing wall 112. The friction area 132 of the housing wall
`112 lies opposite this friction area 131 wherein a friction
`lining 133 is mounted between the two friction areas 131 and
`132.
`Radially inside the
`friction surface
`131
`the
`substantially radially aligned arm. 143 is connected by
`rivets 144 to a component 125 forming biasing areas for the
`energy accumulators
`119.
`This
`component
`125 has
`a
`substantially Ueshaped cross-section whose one arm 125a
`extends radially further inwards
`in order to allow the
`component 125 to be rivetted to the drive part 123 by rivets
`144.
`As can be seen in particular from Figure 3,
`the
`component 125 has in the diameter range of its rivetting a
`substantially larger
`extension in the circumferential
`direction than in the diameter range which is formed to bias
`the energy accumulators 119. The two arms 125a, 125b of the
`U—shaped component 125 extend in the radial direction over
`the entire radial extension of the energy accumulators 119
`
`wherein the axially aligned area connecting the two arms
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`125a and 126b together is mounted radially outside of the
`
`$P12T4. P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 20
`
`Valeo Exhibit 1013, pg. 20
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`

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`outer diameter of the energy accumulators 119.
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`-16-
`
`The energy accumulators 119 are supported at least through
`
`centrifugal force on the support dishes 145 which enclose
`
`the energy accumulators 119 at least over parts of their
`
`outer circumference, and which in turn can be supported in
`
`the radial direction on the axially aligned section 122 of
`
`the drive part 123.
`
`The support dishes 145 each extend
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`circumferentially between two adjoining biasing parts 125
`
`and are held both circumferentially and axially through
`
`these through corresponding recesses
`
`in their axially
`
`aligned connecting area between the two arms 125a and 125b.
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`The arms 125a and 125b of the biasing part 125 forming the
`
`biasing areas for the energy accumulators 119 can be made
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`hardened in order to reduce the wear.
`
`The output part of the rotationally elastic dampener 116 is
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`formed by a f1ange—like component 134 which has on its outer
`
`periphery radial extensions 135
`
`for biasing the energy
`
`accumulators 119.
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`In the rest state of the device 101 these
`
`extensions 135 are located axially between the two arms 125a
`
`and 125b of the biasing component 125 and are enclosed to
`
`some extent by this U.
`
`The arrangement of
`
`the energy
`
`accumulators 119 and of the parts 135 and 125 biasing same
`
`can again be designed so that starting from ‘the zero
`
`position of
`
`the device at first a certain turning is
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`possible without compressing the energy accumulators 119.
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`In its radially inner area the flange 134 is fixedly
`
`connected to the hub 114 , as described in the example with
`
`a welded seam. Radially outside of this welded area,
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`thus
`
`outside the connecting area with the hub 114 a run-up disc
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`137 is mounted between a radially aligned section of the
`
`flange 134 which faces the housing wall 112 and the housing
`
`wall 112 itself.
`
`The run~up disc 137 is again fixed
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`SP1274.P3
`23 September 1993
`
`Valeo Exhibit 1013, pg. 21
`
`Valeo Exhibit 1013, pg. 21
`
`

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`..
`
`1_7
`
`..
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`circumferentially by axially extending areas
`
`138 which
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`engage in corresponding recesses of the flange 134.
`
`When the converter bridging clutch 118 is closed a pressure
`
`chamber 130 is formed which is restricted in one axial
`
`direction by the housing wall 112 of the housing dish 105
`
`and in the opposite axial direction by the turbine wheel 113
`and intermediate part 140. Sealing the pressure chamber is
`
`carried out radially inside in the area of the hub through
`the seal 141,
`furthermore on the radially inner centring
`area of
`the turbine wheel 113 through the seal 147 and
`
`the
`radially outside through the friction areas 131 of
`radially extending arm 143 and 132 of the housing wall 112
`wherein a friction lining 133 is mounted between these
`
`friction areas. The seals 141 and 147 can advantageously be
`
`formed by so—called 0-rings.
`
`The converter bridging clutch 118 is closed by the pressure
`produced by the fluid, such as for example oil, contained in
`the i