(12)
`
`Patent(19)GB_(11)2
`
`123(13)B
`
`Title of Invention
`
`A torsion damping device with a dynamic
`vibration damper, in particular for automotive
`vehicles
`
`INT GL5; F16D 3/1 2 3/1 4
`
`lnventor(s)
`Michel Graton
`Michel Glzard
`Roger Carmlllet
`
`Proprietor(s)
`Valeo
`
`(Incorporated In France)
`
`43 Rue Bayen
`75848 Paris
`Oedex 17
`France
`
`Agent and/or
`Address for Service
`Page White 8: Farrer
`54 Doughty Street
`London
`‘WC1 N 2LS
`
`United Kingdom
`
`Application No
`9008763.6
`
`Date of filing
`1 9.04.1990
`
`Priority Data
`
`(31 )
`
`05638
`
`(32)
`
`28.04.1989 .
`
`(33)
`
`FR
`
`Application published
`07.1 1 .1 990
`
`Patent published
`31.03.1993
`
`Domestic classification
`(Edition L)
`F2U U224 U286 U314 U340
`U396 U398 U399
`F25 SCK S802 3814
`U1 5 $2014
`
`Documents cited
`None
`
`Field of search
`
`As for published application
`2231123 A Viz:
`
`UK CL(Edition J ) F2U
`INT CL‘ F16D 3/00
`updated as appropriate
`
`Valeo Exhibit 1025, pg. 1
`
`Valeo Exhibit 1025, pg. 1
`
`
`
`Patent(19)GB_(11)2
`
`123(13)B
`
`Title of Invention
`
`A torsion damping device with a dynamic
`vibration damper, in particular for automotive
`vehicles
`
`INT GL5; F16D 3/1 2 3/1 4
`
`lnventor(s)
`Michel Graton
`Michel Glzard
`Roger Carmlllet
`
`Proprietor(s)
`Valeo
`
`(Incorporated In France)
`
`43 Rue Bayen
`75848 Paris
`Oedex 17
`France
`
`Agent and/or
`Address for Service
`Page White 8: Farrer
`54 Doughty Street
`London
`‘WC1 N 2LS
`
`United Kingdom
`
`Application No
`9008763.6
`
`Date of filing
`1 9.04.1990
`
`Priority Data
`
`(31 )
`
`05638
`
`(32)
`
`28.04.1989 .
`
`(33)
`
`FR
`
`Application published
`07.1 1 .1 990
`
`Patent published
`31.03.1993
`
`Domestic classification
`(Edition L)
`F2U U224 U286 U314 U340
`U396 U398 U399
`F25 SCK S802 3814
`U1 5 $2014
`
`Documents cited
`None
`
`Field of search
`
`As for published application
`2231123 A Viz:
`
`UK CL(Edition J ) F2U
`INT CL‘ F16D 3/00
`updated as appropriate
`
`Valeo Exhibit 1025, pg. 1
`
`Valeo Exhibit 1025, pg. 1
`
`
`
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`Valeo Exhibit 1025, pg. 2
`
`Valeo Exhibit 1025, pg. 2
`
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`Valeo Exhibit 1025, pg. 3
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`Valeo Exhibit 1025, pg. 3
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`
`Valeo Exhibit 1025, pg. 4
`
`Valeo Exhibit 1025, pg. 4
`
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`
`Valeo Exhibit 1025, pg. 5
`
`Valeo Exhibit 1025, pg. 5
`
`
`
`A TORSION DAMPING DEVICE WITH A DYNAMIC VIBRATION DAMPER,
`IN PARTICULAR FOR AUI6fi6IIVE UEHIEEES
`
`This invention relates to torsion damping devices,
`
`in‘
`
`particular for automotive vehicles, such a device being of
`
`the kind comprising two coaxial parts which are mounted for
`
`movement of one with respect to the other within the limits
`
`of a predetermined angular displacement and against the
`
`action of circumferentially acting resilient means and
`
`against the action of damping means.
`
`conventionally, one of the said parts comprises two guide
`
`rings which are arranged on either side of a damper plate
`
`which is part of the other one of the two said parts.
`
`The
`
`damper plate or the guide rings are secured to a hub for
`
`rotation therewith, with, optionally, a facility for an
`
`initial clearance to be taken up before rotation with the
`
`hub takes place.
`
`As is well known,
`in engines of the reciprocating type,
`in
`which the power output is delivered in the form of periodic
`
`impulses, due to the expansion of a gas against pistons
`
`which actuate a crankshaft by means of connecting rods,
`
`the
`
`variations in engine torque and inertia torque arising from
`
`the various components of the engine which are set in
`
`reciprocating motion usually make it necessary to provide a
`
`flywheel
`
`in order to smooth out the speed.
`
`In order to reduce the vibrations which occur,
`
`in
`
`particular in the region of the pressure plate of the
`
`clutch when the latter is being disengaged,
`
`the published
`
`patent application No. DE 3 609 048A of the Federal
`
`Republic of Germany proposes to equip the flywheel with a
`
`dynamic vibration damper. This damper is effective in the
`
`frequency range which includes the resonant frequency of
`
`Valeo Exhibit 1025, pg. 6
`
`Valeo Exhibit 1025, pg. 6
`
`
`
`the pressure plate when the latter is not in gripping
`
`engagement with the friction disc of the clutch.
`
`Such an arrangement is well adapted for damping out engine
`
`vibrations, and in particular the axial vibrations of the
`
`crankshaft. However, it is not entirely satisfactory:
`
`it
`
`does not allow the natural frequencies in torsion of the
`
`whole of the kinematic transmission train which couples the
`
`engine to the road wheels, and which includes the gearbox,
`
`to be suppressed. Accordingly, it does not allow the
`
`critical vibrations which occur in the region of the
`
`resonant frequency of the transmission train to be
`
`eliminated in certain vehicles at given engine speeds when
`
`the clutch is engaged.
`
`In addition, such a damper is
`
`arranged to extend over a circumference of large diameter,
`
`so that it is necessary to provide some suitable means
`
`preventing its mass from flying off under the effect of
`
`centrifugal force. Besides which,
`
`this arrangement
`
`requires modification of the reaction plate or flywheel of
`
`the clutch.
`
`It has also been proposed,
`
`in United Kingdom published
`
`patent application GB 2 157 398A,
`
`to suppress the
`
`vibrations when the engine is in an idling mode,
`
`that is to
`
`say when the transmission is not under load,
`
`this being
`
`achieved by means of a mass which is welded on to a support
`
`mounted on the hub by means of a friction coupling. This
`
`particular arrangement is not adapted to remove the
`
`critical vibrations which occur under load when the clutch
`
`is engaged,
`
`in certain vehicles in the vicinity of a
`
`resonant frequency, for example at engine speeds of 1500 to
`
`2800 rev/min which are lower than the maximum engine speed.
`
`In order to overcome this problem, it might be thought
`
`Valeo Exhibit 1025, pg. 7
`
`Valeo Exhibit 1025, pg. 7
`
`
`
`possible to increase the mass of the reaction plate. This is
`however not satisfactory, since it leads to an increase in
`fuel consumption of the vehicle and to a reduction in
`performance,
`in terms of its ability to accelerate.
`
`It could also be supposed that the engine torque might be
`
`reduced. This is no more satisfactory.
`
`a torsion damping device
`In accordance with the invention,
`comprising two coaxial parts which are mounted for movement of
`one with respect to the other within the limits of a
`predetermined angular displacement and against the action of
`resilient means and against the action of a damping means,
`
`with one of the said coaxial parts comprising a hub fixed with
`
`the other of
`respect to a drive shaft for rotation therewith,
`said coaxial parts comprising two guide rings and a damper
`plate,
`the guide rings being disposed on either side of the
`damper plate, one of the damper plate and the guide rings
`being adapted to rotate with the hub, wherein a dynamic
`vibration damper, which comprises a weight which is connected
`by means of at least one resilient element to a support,
`is
`adapted to rotate with.the hub,
`the natural frequency of the
`dynamic vibration damper being determined by the resonant
`frequency of the torsion damping device mounted on the drive
`shaft, so as to damp vibrations of the torsion damping device.
`
`the mass of the dynamic
`By virtue of this arrangement,
`vibration damper
`(sometimes called a dynamic absorber)
`
`is
`
`determined by, for example,
`
`in the context of a friction
`
`Valeo Exhibit 1025, pg. 8
`
`Valeo Exhibit 1025, pg. 8
`
`
`
`in such a way that
`inertia of the gearbox,
`the
`clutch.
`there is no need to provide any retaining means for this
`mass, and also so that the critical vibrations that occur
`in the transmission train between the engine and the road
`wheels at the said resonant frequency are attenuated.
`The
`‘natural frequency of the dynamic vibration damper is then
`determined by the resonant frequency of the torsion damphm dance
`mounted on its drive
`shaft.
`
`leaves the_
`It will be appreciated that this arrangement
`and that the dynamic
`
`vibratio
`
`friction clutch.
`
`ZODE: .
`
`The resilient element may be in the form of a block of
`elastic material, chosen so that its inherent damping
`ability is favourable to the suppression of the vibrations.
`In a modification, it may take the form of a spiral spring
`having an arm carrying the working mass and being joined to
`an internal carrying element constituting the said support.
`irst embodiment of the invention,
`the
`er may be mounted directly on the’
`for example by crimping.
`In a
`ed on an intermediate
`
`In accordance with.a f
`support of the said damp
`hub to which it is secured,
`further modification it may be mount
`member which is itself secured to the hub.
`
`the support may be secured to a
`In a third embodiment,
`bearing which is coupled with the hub for rotation
`therewith, optionally after a clearance has been taken up.
`This arrangement enables a conventional torsion damping
`device to be modified as little as possible.
`
`In accordance with a preferred-feature of the invention,
`
`the
`
`Valeo Exhibit 1025, pg_ 9
`
`Valeo Exhibit 1025, pg. 9
`
`
`
`dynamic vibration damper is associated with a viscous
`damping device. This enables the damping effect of the
`viscous damping device to be improved in the region of the
`resonant frequency, so that the vibrations will be
`suppressed more effectively.
`The description which follows, which is given by way of
`example only,
`illustrates the invention in the context of a
`friction clutch for automotive vehicles, with reference to
`the accompanying drawings,
`in which:-,
`Figure llis a view in axial cross section of a torsioncmm inP
`device
`in accordance with the invention,
`showing three
`alternative forms of dynamic vibration damper;
`
`9
`
`Figure 2 is a view similar to Figure 1, but showing another
`embodiment of the invention;
`
`a simplified view showing.the arrangement of
`Figure 3 is
`resilient means of low stiffness which,
`in Figure 1, are
`mounted between the hub and the damper plate of the torsion
`
`damper;
`
`indicated, so as to illustrate in general terms a group of
`further embodiments of the invention;
`and
`
`‘gures 1 and 2, but
`bodiments that
`
`In the embodiments shown in the drawings a friction clutch is
`used to illustrate one example of a torsion damping device.
`The friction clutch comprises two coaxial clutch parts A and
`B, which are mounted for mutual relative rotation within the
`limits of a predetermined angular displacement and against the
`
`Valeo Exhibit 1025, pg. 10
`
`Valeo Exhibit 1025, pg. 10
`
`
`
`action, both of circumferentially acting resilient means 1
`
`and of a damping means 2.
`
`The clutch part A is a passive or driven part of the
`clutch.
`It comprises a hub 3 which has an internal bore
`
`which is splined for mounting on the input shaft of the
`
`gearbox BV (Figure 4), so as to drive this input shaft in
`
`rotation.
`
`The clutch part B, which is the active or
`
`driving part of the clutch, comprises two guide rings 4 and_
`
`5 which are connected together in spaced apart relationship
`
`by means of axial spacers 7, which in this example are in
`
`the form of spacer bars.
`
`The guide rings 4 and 5 are
`
`mounted for free rotation around the hub 3.
`
`The guide ring 5 carries a clutch disc 6 which is fitted
`
`with friction liners 9,
`
`the clutch disc 6 being connected
`
`with the guide rings 4 and 5 by means of the spacer bars 7.
`
`The clutch disc 6 is laid against the guide ring 5 and
`
`secured to the latter by the spacer bars 7.
`
`The driving
`
`clutch part B is coupled with the internal combustion
`
`engine M (Figure 4) of the vehicle, so as to be rotated by
`
`the engine. This coupling is achieved in the usual way by
`
`gripping of the friction liners 9 between the pressure
`
`plate and reaction plate of the clutch, neither of which is
`
`shown.
`
`Windows 10 and 11 are formed respectively in a damper plate
`
`8 and in the guide rings 4 and 5.
`
`The above mentioned
`
`circumferentially acting resilient means 1 consist,
`
`in this
`
`example, of coil springs which are mounted without any
`
`clearance in the windows 11 and, optionally with a
`
`clearance, also in the windows 10 so that the springs 1 can
`
`act in stages.
`
`The damper plate 8 is mounted for rotational movement with
`
`Valeo Exhibit 1025, pg. 11
`
`Valeo Exhibit 1025, pg. 11
`
`
`
`respect to the hub 3. by means of a loose coupling means 12
`
`and resilient means 13 of low stiffness, mounted between
`
`the damper plate 8 and hub 3.
`
`In this example the
`
`resilient means 13 are in the form of coil springs as
`
`generally described in French published patent application
`
`No. FR 2 560 328A.
`
`In the present example, as illustrated
`
`in Figure 3,
`
`the loose coupling means 12 comprise firstly a
`
`plurality of trapezoidal teeth and secondly a plurality of
`
`complementary recesses.
`
`Each of these teeth extends, with
`
`a circumferential clearance,
`
`into a corresponding one of
`
`the recesses.
`
`The teeth and recesses are formed partly on
`
`the inner periphery of the damper plate 8 and partly in a
`
`flange 16 which constitutes a thickened portion of the
`
`outer periphery of the hub 3.
`
`On each of the members 3 and
`
`8,
`
`the teeth and recesses alternate with each other.
`
`The
`
`springs 13 are of lower stiffness than the springs 1.
`
`In
`
`this example there are two springs 13, diametrically
`
`opposed to each other and mounted partly in slots 15 formed
`
`in the damper plate 8 and partly in similar slots in the
`
`flange 16 of the hub 3. Thrust inserts 14 are provided
`
`between the ends of the springs 13 and the end thrust
`
`surfaces of the slots 15.
`
`The damper plate 8 is arranged axially between the guide
`
`rings 4 and 5, and has apertures 17 through which the
`
`spacer bars 7 extend.
`
`The friction means 2 comprise an annular centring bearing
`
`18 with an L—shaped cross section, which is inserted so as
`
`to extend axially between the damper plate 8 and the clutch
`
`disc 6, by virtue of a transverse portion of the bearing
`
`that acts as a spacer.
`
`The bearing 18 extends radially
`
`between the outer periphery of the hub 3 and the inner
`
`peripheral surface of the guide ring 5 by virtue of an
`
`Valeo Exhibit 1025, pg. 12
`
`Valeo Exhibit 1025, pg. 12
`
`
`
`axial locating portion of the bearing that carries the
`
`bearing surface itself, freely engaging around the hub 3.
`
`This bearing 18 is preferably made of fibre reinforced
`
`plastics material.
`
`It may however alternatively be made of
`
`a metal, for example of bronze.
`
`A friction ring 19 is inserted axially between the damper
`
`plate 8 and the guide ring 4.
`
`It is preferably made of a
`
`plastics material, and is provided with bosses which are
`
`engaged in corresponding holes formed in the guide ring 4,
`
`so as to couple the ring 19 in rotation with the latter.
`
`The two guide rings 4 and 5 are of a standard type.
`
`The
`
`bearing 18 also has similar bosses, which are engaged in
`
`corresponding holes formed in the guide ring 7 and in the
`
`clutch disc 6, so that the bearing is thereby coupled for
`
`rotation with them (Figure 1).
`
`Another bearing 20, again having an L-shaped cross section,
`
`is inserted so as to extend radially between the guide ring
`
`4 and the hub 3, and axially between the guide ring 4 and
`
`the flange 16.
`
`The bearing 20 is rotatable with the guide
`
`ring 4, by virtue of bosses, each of which is engaged in a
`
`respective one of a set of complementary recesses formed in
`
`the guide ring 4.
`
`A resilient biassing ring 21 is associated with the
`
`friction ring 19.
`
`The resilient ring 21, which is in the
`
`form of a Belleville ring, bears on the guide ring 4 so as
`
`to urge the friction ring 19 towards the damper plate 8,
`
`and so as also to cause the bearing 18 to be gripped
`
`between the damper plate 8 and the guide ring 5.
`
`Similarly, a second resilient biassing ring 22 is
`
`associated with the bearing 20, with the ring 22 bearing
`
`axially on the guide ring 4 and urging the bearing 20
`
`Valeo Exhibit 1025, pg. 13
`
`Valeo Exhibit 1025, pg. 13
`
`
`
`axially towards the flange 16.
`
`The clutch disc 6, with its friction liners 9,
`coupled with the hub 3 via two damnng devnms.
`One of the latter, which will be called the main damper,
`
`is thus
`
`comprises the spr
`and 21, while the other damper,
`the loose coupling
`predamper, comprises the springs 13,
`means 12 and the bearing 20 with its associated ring 22.
`
`In a first stage of the angular displacement between the
`clutch disc 6 and the hub 3.
`the guide rings 4 and S are
`fixed with respect to the damper plate 8,
`to the extent
`that the clearance
`”'
`_
`'
`means 12
`has not yet been taken up and the springs 13 are
`compressed, while the bearing 20 transmits the appropriate
`forces. Once the clearance in the loose coupling means has
`been taken up under load.
`the damper plate 8 becomes
`displaced with respect to the guide rings A and 5, against
`the action of the springs 1 and the damping means 2.
`The
`springs 13 then remain in their compressed state.
`
`A dynamic vibration damper or absorber 30 is linked with
`the hub 3.
`The absorber 30 comprises a weight 33 which is
`connected through at least one resilient element 32 to a
`support 31, The latter is coupled with the hub 3 for
`In some embodiments, as will be
`.
`'
`aken up before
`‘
`'
`seen,
`the support 31 rotates with the hub.
`The natural frequency
`of vibration of the dynamic vibration damper 30 is detemmned by
`
`In Figure 1,
`
`the support 31 is fast
`
`Valeo Exhibit 1025, pg. 14
`
`Valeo Exhibit 1025, pg. 14
`
`
`
`in this ekample by a force fit as will be described
`3,
`The support 31 is made of metal,
`below, and by crimping.
`y be screwed to the hub.
`The
`d of the median axis of the
`
`and in a modification it ma
`
`weight 33 lies radially inwar
`level with the radially inner part of the
`d its inner periphery is_
`
`springs 1,
`It is annular in shape an
`
`provided with a radial flange for secur
`which consists of a block of
`the resilient element 32,
`This block 32
`elastic material, for example an elastomer.
`
`ing the weight to
`
`vibrations, and
`
`but also to the support 31.
`
`The natural frequency of the damper 30 depends on the
`particular application, and in particular on the gearbox,
`and is chosen so as to be close to, and therefore adapted
`F the friction clutch mounted on
`to or determined by the natural frequency 0
`This natural frequency depends in
`which act under load when the
`
`the drive
`
`shaft.
`
`addition on the springs 1,
`and also on the hub 3, damper plate 8,
`clutch disc 6 and friction liners 9.
`
`clutch is engaged,
`
`guide rings 4 and 5,
`
`modification it may for exam
`
`like the
`’the block 32 is of an annular shape;
`The block 32 may be
`
`In Figure 1,
`weight 33, as is also the support 31.
`In another
`divided into a plurality of distinct parts.
`ple be in the shape of an
`the block 32 is adhesively
`In this example,
`annular comb.
`secured both to the weight 33 and to the support 31. This
`is achieved by in situ vulcanisation of an appropriate
`rubbery mass between the weight 33 and the support 31.
`
`The support 31 has a plurality of teeth on its inner
`It is secured
`and is harder than the hub 3.
`3 by being force fitted into
`
`periphery,
`against rotation on the hub
`
`Valeo Exhibit 1025, pg. 15
`
`Valeo Exhibit 1025, pg. 15
`
`
`
`the hub; with'the teeth of the support 31 making
`It is secured against axial
`indentations in the hub 3.
`In a
`movement on the hub by being crimped to the latter.
`modification,
`the block 32 is secured to the weight 33 and
`also to the support 31 by application of an adhesive
`material, or in any other suitable way.
`
`In the lower part of Figure 1, a modified form of dynamic
`vibration damper is shown in which the weight 33 has a
`central opening for the block 32 to be secured in the
`port 31 has a cranked or
`
`to the guide ring 5, so that the axial bulk of the assembly
`is reduced. This cranked form is given by an axial
`displacement of the outer periphery of the support 31
`towards the guide ring 5.
`
`the guide rings 4 and
`In the embodiment shown in Figure 2,
`in this example by
`5 are secured directly to the hub 3,
`crimping.
`The damper plate 8 is mounted on the hub 3 so as
`t to the latter, and carries
`to rotate freely with respec
`The loose
`the clutch disc 6 with its friction liners°9.
`with its optional.clearance,
`
`is absent
`
`coupling means 12,
`
`from this embodiment.
`
`Advantage is taken_of this arrangement to secure the block
`32 directly on to the guide ring 5.
`The weight 33, which
`rings 4 and S and the
`is annular in shape like the guide
`has on its outer periphery a chamfered
`
`damper plate 8,
`
`may,
`
`separate parts.
`
`In a modification as illustrated in the lower part of Figure 1 it
`
`is the damper plate 8
`
`VVa|eo Exhibit 1025, pg. 16
`
`Valeo Exhibit 1025, pg. 16
`
`
`
`which constitutes the support for the block 32 and the mass
`
`33,
`
`the dynamic damper then being disposed between the two
`
`guide rings & and S.
`
`In the arrangement shown diagrammatically,
`
`in general
`
`terms,
`
`in Figure 4 and in specific examples in Figures 5 to
`
`8,
`
`the dynamic damper (or dynamic absorber) 30 is
`
`associated with a viscous damping device 40. This device
`
`40 is confined within a sealed chamber.
`
`This chamber is
`
`filled with a viscous fluid, and in particular a fluid of
`the "non Newtonian” type, which is characterised by good
`stability of its viscosity with variation in temperature,
`
`and a dynamic viscosity which reduces as a function of the
`
`speed gradient.
`
`An example of such a fluid is a silicone.
`
`This arrangement enables the damper 30 to act on the device
`
`40 in such a way as to suppress the vibrations more
`
`rapidly.
`
`In the diagram of Figure 4, various possible positions of
`
`the damper 30 are shown,
`
`together with the springs 1 and 13
`
`which are indicated symbolically,
`
`The references_f and fp
`
`correspond respectively to the frictional action of the
`main damper and the frictional action of the predamper,
`block 32 being indicated.diagrammatically with its
`stiffness and its internal damping effect.
`
`the
`
`Referring now to Figure 5,
`
`in this embodiment the vibration
`
`damper 30 is arranged, as in the other Figures, outside the
`
`volume delimited by the guide rings A and S, at the end of
`
`the hub 3 which is at the right of the Figure.
`
`The viscous
`
`damping device A0 is disposed at the level of the left hand
`
`end of the hub 3, again outside the volume delimited by the
`
`guide rings 4 and S, and generally in the manner described
`
`in U.K. patent application No. 2227810.
`
`‘
`
`Valeo Exhibit 1025, pg. 17
`
`Valeo Exhibit 1025, pg. 17
`
`
`
`~The device 40 lies wholly within a housing 41, which
`
`comprises two housing parts 42 and 43, arranged to be
`
`moveable circumferentially with respect to each other.
`
`The
`
`first housing portion 42 comprises two face plates, which
`
`are generally spaced apart from each other but which are
`
`mated together at their outer periphery and secured to a
`
`carrier plate 45, by means of fastening members such as
`
`rivets or bolts.
`
`The second housing part 43 comprises a disc which is
`
`disposed between the two face plates of the first housing
`
`part 42.
`
`A seal 44 is provided at the internal periphery
`
`of the disc 43 for sealingly closing the housing 41.
`
`The
`
`seal 44 cooperates frictionally with the two face plates of
`
`the housing 41.
`
`The disc 43 is secured by crimping it to
`
`the hub 3.
`
`The plate 45 has tabs 46 which are engaged on
`
`the heads of the spacer bar 7, so as to fasten the housing
`
`41 to the guide rings 4 and 5 for rotation with the latter.
`
`The housing 41 is thus carried by the hub 3, while the tabs
`
`46 and the spacer bars 7 constitute a mutual engagement
`
`means between the guide rings 4 and 5 on the one hand and
`
`the housing part 42 on the other.
`
`It is of course possible
`
`to locate the damper 30 on the same side of the clutch as
`
`the damping device 40, as is shown in the lower part of
`
`Figure 5.
`
`Referring now to Figure 6,
`
`the viscous damping device 40
`
`here comprises a housing 41 in the form of two half shells,
`
`one of which has at its inner periphery a radial extension
`
`47 which is secured by crimping it to the hub 3.
`
`The disc
`
`43 is connected to the guide rings 4 and 5 for rotation
`
`therewith, but the mutual engagement means in this
`
`embodiment comprise a member 48 which is fastened by
`
`welding to the guide ring 5.
`
`The member 48 has tenons to
`
`give axial orientation, which are engaged in corresponding
`
`Valeo Exhibit 1025, pg. 18
`
`Valeo Exhibit 1025, pg. 18
`
`
`
`mortices formed on the inner periphery of the disc 43.
`
`The
`
`radial length of the disc 40 may be increased if desired.
`
`The damper 30 is thus secured directly on to the half shell
`
`which does not have the extension 47.
`
`The block 32 is
`
`directly adhered on this same half shell.
`
`The damper 30
`
`extends radially beyond the springs 1, and its weight 30 is
`
`made with a somewhat serpentine cross section so as to
`
`adapt it to follow the contour of the bent out ears at the
`
`edges of the windows 11. This arrangement allows the axial
`
`length of the assembly to be reduced.
`
`It is of course possible, as an alternative, and as seen in
`
`the lower part of Figure 6,
`
`to secure the damper 30 to the
`
`other half shell.
`
`In that case,
`
`the main part of the
`
`weight 33, with its radial flange for external fastening,
`
`is arranged radially inwardly of the block 32.
`
`while,
`
`in the foregoing Figures,
`
`the damper 30 was secured
`
`directly to the hub 3,
`
`in Figures 7 and 8 the damper 30 is
`
`secured to the bearing 18.
`
`To this end,
`
`the latter has a
`
`plurality of bosses 50 which engage in corresponding holes
`
`52 formed in the damper plate 8, so as to secure the
`
`bearing 18 to the latter, for rotation therewith.
`
`A
`
`clearance.
`
`The bearing 18 extends around the hub 3 but is
`
`free to rotate with respect to the latter, and has at its
`
`inner periphery an annular portion 49 for axial
`
`orientation.
`
`The support 31 is secured,
`
`for example by
`
`crimping,
`
`to this portion 49.
`
`As will be understood from the foregoing,
`
`this arrangement
`
`avoids adding the inertia of the damper 30 to that of the
`
`hub 3 so long as the clearance in the loose coupling means
`
`12 has not yet been taken up.
`
`The springs 13 can then be
`
`given a lower value of stiffness than in the arrangements
`
`Valeo Exhibit 1025, pg. 19
`
`Valeo Exhibit 1025, pg. 19
`
`
`
`shown in the previous Figures.
`
`Referring now to Figure 7, this shows two embodiments of
`
`the damper 30,
`
`identical to those shown in Figure 1.
`
`In Figure 8,
`
`the viscous damping device 40, which is
`
`identical to that shown in Figure 5,
`
`is again secured to
`
`the bearing 18, with the disc 43 being secured by crimping
`
`to the bearing portion 49.
`
`The vibration damper 30 may be secured directly on to the
`
`hub 3, for example by crimping, or alternatively on to the
`
`bearing 18, which then has for this purpose a second
`annular portion 51 oriented radially.
`
`By virtue of these arrangements, it will be seen that in
`
`Figure 8 it is only during a second stage of operation that
`
`the viscous damping means 40 operates, since in the first
`
`stage there is no relative movement between the damper
`
`plate 8 and the guide rings 4 and 8.
`
`theibosses 50 may extend
`As has already been mentioned,
`into the holes 52 with a clearance;
`this enables the
`viscous damper to begin operating later. Similarly,
`
`the
`
`disc 43 may be provided with teethfwhich penetrate, with a
`clearance,
`into complementary teeth formed on the bearing
`18, as can be seen in the lower part of Figure 8. This
`arrangement enables the viscous damping means 40
`to
`
`operate like a sliding drawer, with the facility to act
`
`during the relative angular displacement which takes place
`
`A clearance may
`‘between the hub 3 and the damper plate 8.
`also be provided between the tabs 46 and the spacer bars 7.
`
`In a further modification, not shown,
`
`the viscous damping
`
`means 40 includes a plurality of fins of generally
`
`Valeo Exhibit 1025, pg. 20
`
`Valeo Exhibit 1025, pg. 20
`
`
`
`trapezoidal cross section,
`
`forming two groups mounted in a
`
`head-to—toe relationship and extending generally in radial
`
`‘planes passing through the axis of the assembly.
`
`Any one
`
`fin of one group is then interleaved circumferentially
`
`between two fins of the other group,
`
`in the manner
`
`described and shown for example in Figure 4 of French
`
`published patent application FR 2 597 181A.
`
`In yet another
`
`modification,
`
`the viscous damper 40 may be mounted between
`
`the guide rings 4 and 5, radially inwardly of the springs
`1.
`
`It will be clear from the foregoing description and the
`
`drawings that the weight 33 and block 32 of the damper 30
`
`will be dimensioned according to the application to which
`
`the clutch is to be put,
`
`in such a way that the damper 30
`
`operates in the range of resonant frequencies of the
`torsion damping device mounted on the driven shaft and
`
`therefore influenced by the gearbox.
`
`In practice,
`
`the
`
`amplitudes of the vibrations at the resonant frequency are
`
`reduced;
`
`and the appearance of two resonant frequencies.
`
`in the vicinity of the natural frequency, may be envisaged.
`
`The present invention is of course not limited to the
`
`embodiments described herein.
`
`In particular,
`
`the support
`
`31 may be secured to the hub 3 by means of bolts or the
`
`like, for example.
`
`Again,
`
`the resilient element may comprise a resiliently
`
`deformable arm,
`
`integrally attached through a root zone to
`
`an internal carrying element constituting the support and
`
`carrying the weight 33 at its outer periphery.
`
`As to the
`
`shape of the arm and its carrying element, reference is
`
`invited to French published patent application No.
`
`FR 2 493 446A, for example Figure 22 of the latter:
`
`the
`
`Valeo Exhibit 1025, pg. 21
`
`Valeo Exhibit 1025, pg. 21
`
`
`
`arm may extend over more than 360 degrees in the form of a
`
`The arm may of course carry at its outer periphery
`spiral.
`the block 32 of resilient material,
`in such a way that the
`support 31 may itself be partially resilient.
`The resilient element may of course consist of a plurality
`
`of coil springs, each‘connected to a weight and also to a
`
`spacer secured to the support.
`
`The predamper may be arranged axially between the damper
`plate Brand the guide ring 5,
`in the manner described for
`example in'French_ published patent applicationjNo.. 2613800.
`The
`damper plate 8 may be split in the manner {described in
`
`French published patent application No.
`
`FR‘ 2 566 497A.
`
`:Va|eo Exhibit 1025, pg. 22
`
`Valeo Exhibit 1025, pg. 22
`
`
`
`1.
`
`A torsion damping device comprising two coaxial parts
`
`‘which are mounted for movement of one with respect
`other within
`the
`limits
`of
`a
`predetermined
`
`to the
`angular
`
`and
`resilient means
`the action of
`and against
`displacement
`against
`the action of
`a damping means, with one of
`the said
`coaxial parts comprising a hub fixed with respect
`to a drive
`shaft for rotation therewith,
`the other of said coaxial parts
`
`comprising two guide rings and a damper plate,
`
`the guide rings
`
`the
`the damper plate, one of
`being disposed on either side of
`damper plate and the guide rings being adapted to rotate with
`the hub, wherein a dynamic vibration damper, which comprises a
`
`weight which is connected by means of at
`
`least one resilient
`
`element to.a support,
`
`is adapted to rotate with the hub,
`
`the
`
`natural
`
`frequency
`
`of
`
`the
`
`dynamic vibration damper
`
`being
`
`determined km’
`
`the resonant
`
`frequency of
`
`the torsion damping
`
`device mounted on the drive shaft,
`
`so as to damp vibrations of
`
`the torsion damping device.
`
`A device according to Claim 1, wherein the support
`2.
`fixed to the hub.
`
`is
`
`A device according to Claim 1, wherein the damper plate
`3..
`is adapted to rotate with the hub via a bearing,
`the support
`
`is fixed to the bearing for rotation therewith, and the damper
`
`plate is mounted relative to the hub by a coupling means.
`
`4.
`
`A device according to Claim 1,
`
`2 or 3 wherein the one of
`
`the damper plate and guide rings is adapted for rotation with
`
`the hub after a clearance has been taken up.
`
`Valeo Exhibit 1025, pg. 23
`
`Valeo Exhibit 1025, pg. 23
`
`
`
`5.
`
`A device according to Claim 3, wherein the bearing is
`
`adapted for rotation with the damper plate after a clearance
`
`has been taken up.
`
`6.‘
`
`A device according to any one of Claims
`
`1
`
`to 5, wherein
`
`the dynamic vibration damper
`
`is vassociated with a viscous
`
`damping means which is connected to the hub,
`
`for
`
`rotation
`
`therewith.
`
`7.
`
`A device
`
`according to Claim 6, wherein
`
`the viscous
`
`damping means
`
`is adapted for
`
`rotation with the hub after
`
`a
`
`clearance has been taken up.
`
`8.
`
`A device according to Claim 6 or 7,
`
`in which the viscous
`
`damping means includes a housing,
`
`the dynamic vibration damper
`
`being fixed to the housing.
`
`9.
`
`A device according to Claim 6 or 7,
`
`in which the housing
`
`comprises
`
`two half shells, one of
`
`the half shells having a
`
`radial extension for
`
`securing to the hub,
`
`‘with a block. of
`
`resilient material which
`
`constitutes
`
`the
`
`said
`
`resilient
`
`element being secured on one of the two half shells.
`
`10.
`
`A device according to Claim 6 or 7,
`
`in which the viscous
`
`damping means comprises the said housing secured to a bearing
`having an L—shaped cross section and arranged between the hub
`
`and one of the guide rings,
`
`the dynamic vibration damper being
`
`mounted on the said hearing by means of
`
`a portion. of
`
`the
`
`latter.
`
`ll.
`
`A device according to
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