FR2688846A1 - OSCILLATION DAMPING DEVICE. - Google Patents

Abstract

The invention relates to a device for damping vibrations between an engine and a clutch, comprising two flywheel elements (3, 4) which are coupled via a damping system, one of which can be connected to the motor output shaft and the other has a counter-friction surface for driving the clutch friction disc. One of the elements has a ring-shaped housing which is filled with a viscous agent and in which are received and supported in a circumferential direction energy accumulators (45). A disc-shaped component supports the parts delimiting said housing and can be coupled, via radially interior regions, with the output shaft of the motor. Support zones for a disk-shaped flange (41) penetrate into said housing so as to be able to request the energy accumulators and transmit torque to the other element of the flywheel. Application to the automotive field.

Description

The present invention relates to a damping device

  oscillations, in particular between an engine

  and a transmission line, comprising a damping system

  a transition between two flywheel elements, the input portion being constituted by one of the flywheel elements which can be coupled with the motor and the output portion being constituted by the other flywheel element which can be coupled with the transmission line, for example by

via a clutch.

  Devices of this kind have aera-

  as damping means between the flywheel elements as well as energy accumulators, such as

  coil springs acting in a circumferential direction

  rential and accumulating the elastic energy that accumula-

  energy drivers acting in an axial direction and producing frictionally, i.e., hysteresis, co-operation with friction or slip liners parallel to the energy accumulators

  acting in a circumferential direction.

  Devices of this kind obviously make it possible

  in some particular applications, to obtain relatively good improvements in oscillation and noise behavior, but in many

  case, they represent only a compromise solution.

  Thus, these purely mechanical arrangements do not cover the broad spectrum of imperatives to satisfy

  under the different operating conditions, which

  respond to quite different oscillation and noise behaviors They would become all the more complicated and therefore expensive if one tried to satisfy a large number of operating conditions because, for additional domains of amplitudes, it is necessary to involve additional means and always more complicated In particular devices of this kind do not allow to adapt the damping characteristic to several variable operating conditions, inter alia because the associated hysteresis

  different stages of amortization or

  energy accumulators acting in a circumferential direction can not be modified according to existing conditions.

wear and failures.

  In known devices of the aforementioned type,

  it is also possible that it occurs between

  the flywheels a comparative relative elastic torsion

  For this reason, at least in a wide range of this relative rotation, the damping rate of the damping means acting between the elements of

  The steering wheel is relatively large In many applications

  However, it would be advantageous, in order to obtain a better damping of the oscillations, that it occurs between the elements of large relative rotation flywheel.

  because we could thus better dampen oscillations-

tions of great amplitude.

  The object of the invention is to improve

  such devices, including their cushioning effect

  in order to obtain optimal filtering of the bones

  cations occurring between the engine and the transmission

  both at low speeds of rotation and at

  high speeds, at resonant speeds, when

  during the stopping or under similar conditions In addition, the possibility of adapting the damping characteristic, that is to say

  the degree of energy cancellation, to the different-behavioral

  oscillations and noise of a vehicle in different

  various walking conditions and other influences.

  In addition, the device according to the invention must be able to be manufactured in a particularly simple and inexpensive way. In particular, it must be possible, by measures concerning the construction, to obtain reduced costs of

* 2688846

  using as much as possible of the

  manufacturing process without chip production Also,

  wear must be kept to a minimum and the service life

vice lengthened to the maximum.

  According to the invention, these results are

  obtained by the fact that the device according to the invention

  has at least three of the following features: a) the damping system has at least one annular channel formed by portions of one of the elements of

  flying, at least partially filled with an agent vis-

  as a pasty agent, having a substantially closed cross-section and in which at least two

  accumulators of energy, such as springs, approximately

  in a conînun circle, are housed and supported, b) the annular channel is closed

  a slight interval by a body forming a flange,

  radially in the annular channel, placed in a rotating connection with the second flywheel element and forming the other support zones of the springs,

  (c) the springs between the steering wheel elements

  at least one relative rotation of + 25 degrees, from a central position, d) in the case of "n" springs approximately arranged in a coimun circle, in which case 2 <N <4, the different springs

  70 to 96% of an angular sector, this angular sector

  corresponding to 360 degrees / n,

  (e) the springs extend over 70 to 96% of the

  (f) the springs in the channel-shaped housings are pre-curved at least approximately

  radius of the circle on which they are arranged.

  With the particularities according to the invention, it is possible to obtain an arrangement of the device which ensures a correct guiding of the springs housed in the annular channel so that these springs can be made relatively long and that it is thus possible to To obtain a large relative rotation angle between the two flywheel elements. It is thus possible to better damp the oscillations occurring between the flywheel elements because, because of the relatively large relative rotations.

  as possible between the flywheel elements, the amortization rate

  strain between them may be relatively small for a large relative rotational angle, or even

  for the maximum relative angle of rotation The rate of amor-

  This may be even smaller than the angle

  possible relative rotation is greater.

  Thanks to the arrangement of the device according to the invention, it is thus possible to use long springs in one piece, having a relatively low stiffness, but nevertheless a large elastic race, which

  allow to obtain the low depreciation rate mentioned above.

  Due to the large angle of rotation possible and

  low depreciation rate, it is possible to

  sible to dampen large oscillations as well

  amplitude, or large alternating torques, than oscilla-

  low amplitude, or small alternating pairs.

  Thus in practice, in all engine operating conditions, it is possible to properly damp the

oscillations produced.

  It can be particularly advantageous

  the elasticity rate or the stiffness of the elastic shock absorber

  the spring constituted by the springs between the flywheel elements is of an order of magnitude of between 2 and 20 Nm / degree, preferably between 4 and 15 Nm / degree. It may be particularly advantageous if this elasticity or stiffness exerts in a direction of traction and / or in a thrust direction for a relative rotation angle

  at least 15 degrees between the two steering wheel elements.

  In addition, under the effect of turbulence or

  discharge of the viscous agent placed in the annular channel.

  which occurs during compression and

  tries long springs and also as a result of the movement

  parts of the flange which penetrate the annular channel, to produce a viscous or hydraulic damping which varies as a function of angular velocities or accelerations occurring as a result of variations in

  torque or angular oscillations between the two

  Another advantage is that the damping produced by the viscous agent is variable depending on the rotational speed of the engine. It is thus possible to vary, as a function of the angular speed between the two steering wheel elements. and also depending on the speed of rotation of the device, the damping ratio or the hysteresis, and therefore

  the entire depreciation characteristic of the

  With the aid of the viscous agent placed in the annular channel, it is possible to damp not only oscillations of great amplitude which are generated by strong torque surges by alternating moments, but

  oscillations of small amplitude, which must

  be damped with a corresponding low hysteresis.

  These can be attributed to the fact that the pressure established in the viscous agent is a function of the momentary speed with which a given volume of the viscous agent is repressed. This means that the damping capacity of the viscous agent placed in the annular channel is a function of what happens between the two masses of inertia jerks in the transmitted torque or alternatively large alternating pairs or small variations of couple One can thus get in

  automatic regulation of the damping effect

  ment. With the use of pre-curved springs, it is possible to reduce the tensions occurring therein during their compression and, in addition, to facilitate

mounting.

  The bearing areas of the springs in the annular channel may advantageously be constituted by radial branches formed on the flange and penetrating into the radial zones of the annular channel. The branches may then extend radially outside the bearing zones under the The cleats which, by considering a circumferential direction respectively, the connection of two radial branches can be received in a ring-shaped recess which is connected radially and externally to the channel, in the form of a cleat which clings around the springs in a circumferential direction.

annular.

  The tabs may, in a radial direction, be arranged with respect to the annular channel such that at least when the device is in rotation, the springs rest in the essential

  radially against said cleats.

  advantageous when at least some of the accumulators

  received in the annular channel enter successively.

  in action, that is to say, form a system of amor-

  torsional and multi-stage elastic torsion,

  and when the springs are placed after an angle of rotation

  between the two steering wheel elements are

  initially arranged above the flange in a di-

  circumferential rectification because then, during the angle of rotation

  in which these springs are not

  When they rotate, they rotate with the associated component, in particular the flange, against which they rest radially, so that it is possible to avoid additional damping by friction between the aforementioned springs.

  and the boundary surfaces of the annular channel.

  It is possible to obtain a particularly advantageous structure of the device when the annular channel consists of two shell-shaped bodies, in which case at least one of these bodies may be a profiled sheet metal part. It may be particularly advantageous for the annular channel to consist of two profiled sheet-metal parts in the form of half-shells, in which case these parts may form part of the flywheel element connected to the engine or even constitute this flywheel element. such sheet metal profile parts, compared to

  parts made by chip removal, consists mainly of

  sensibly in a reduction of the manufacturing cost.

  Furthermore, in the case of sheet metal parts manufactured by punching, stamping and stamping, it is possible to produce a large number of advantageous profiles inexpensively, for example also channel sections which deviate from the symmetrical shape. In addition, the circumferential bearings for the springs in the annular channel can be formed by stamped parts or by shaped portions in the form of pockets, so that

  that it is not necessary to provide for additional elements

to fulfill this function.

  The supports or stops provided in the annular channel for the extreme zones of the springs may

  however, be made up in a simple manner by

  elements that are placed in the annular channel, carried out continuously on the periphery.

  may be wedges or platelets

  by shape rivets or by pieces of

welded form.

  With a view to a correct solicitation of the springs

  housed in the annular channel, it is provided in the posi-

  neutral position of the damping or the device on either side of a flange branch, a profiled part

  in the form of a pocket or another stop element.

  To obtain from a central position or a central zone of the two steering wheel elements one

  relative to the other, an elastic damping

  at least in one direction of rotation, it may be advantageous for at least one branch of the flange to have a smaller dimension considering the direction

  periphery that the two supports, planned on both sides

  In this way, the branch and the supports can be arranged relative to one another in the aforementioned initial position of

  in such a way that their areas of solicitation are

  in relation to each other in both directions of rotation.

  tation so as to obtain elastic damping in

  twist and multi-stage in both directions of rotation.

  In the aforementioned initial position, the areas of solicitation

  tion of the limb for the energy accumulator and supports can however also be placed on one side so as to obtain only in one direction of rotation

  torsional and torsional damping.

  The areas of stressing of the branch and the supports can however be shifted between them and with respect to the ends of the springs so that, from

  on either side of the zero position of the relative rotation

  between the two flywheel elements there is no elastic action in a given angle, so that there can be practically no damping effect or only damping

  hydraulic or viscous and / or friction damping

  This depreciation can be very small.

  A reduced dimension of the limb of the flange relative to the supports of the annular channel is advantageous

  in particular in devices in which the one or more

  spells initially not compressed are supported in a

  steering circumferentially by the supports of the annular channel.

  In devices in which accumula-

  energetic latters operating after a rotational anal

  relative rotation between the flywheel elements rotate from this relative angle of rotation with the flange, it may be advantageous for at least one leg of the flange to have a

  dimension considered in a different direction

  In this respect, the zones of stressing of the branch and the supports can be shifted between them only in one direction of rotation.

  but also in both directions of rotation.

  For the operation of the device, it may be particularly advantageous to have at least one

  some of the limbs of the flange and the corresponding ends

  of intermediate layer springs

  have at least one sectional area which is adapted, at least approximately, to the section of the annular channel receiving the springs With such an arrangement of the intermediate layers, these act in the annular channel, during a relative rotation between the two flywheel elements, such as delivery pistons for the viscous agent in this annular channel For better guidance

  spring ends, the intermediate layers may

  have on their side facing the correct end

  spring, an extension penetrating the interior of the springs To allow a commitment

  automatic extensions in the ends of the

  spells, these may include a slightly

  which is followed in the direction of the end by a part having a larger cone angle or a cap shape It can thus be ensured that, in the case where an intermediate layer or a spring cup deviates from a spring end by sliding or ejection, it can occur, upon expansion of the springs or during the biasing of the spring cup, a reengagement of the latter in the spring

  without this or the cup being damaged.

  Because the intermediate layers or the spring cups form delivery pistons in the annular channel for the viscous agent, they can

  advantageously be used for the control of the amor-

  produced by the viscous agent. Thus, it is pos-

  In a particularly simple way, the piston-shaped intermediate layers can be used to determine or adjust the flow rate or the discharge volume of the viscous agent at a determined relative rotation angle between the two components. and thus obtain a well defined damping characteristic curve as a function of determined operating parameters. The variation of the torsion resistance produced by the viscous agent can be generated in a simple manner by varying

  at least one passage section of the viscous agent.

  This can for example be achieved by ensuring that the annular channel does not have a constant section

  at least in partial areas of the longitudinal dimension

  of at least one spring, which is provided to both ex-

  In the case of a relative movement between the annular channel and an intermediate layer, it is thus possible to modify the free section of passage between the annular channel and the intermediate layer as a function of the angle of the intermediate channel. Relative rotation In this respect it may be advantageous if at least some areas of the annular channel in the end portions of the uncompressed springs are enlarged in cross-section with respect to other areas of this channel. progressively within a determined range of relative rotation angles, or it is also possible to provide abrupt section variations. In order to allow the intermediate layers and the energy accumulators to be correctly guided radially outwards, it is advantageous to provide

  such enlargements of section in the zone of the

  inside the annular channel.

  The depreciation produced by the international layers

  in cooperation with the viscous agent can be further modified by performing axial or

  axial recesses in these intermediate layers.

  For the operation of the device, it may be advantageous for the branches of the flange to comprise lugs oriented in a circumferential direction and which

  cling in a recess of the intermediate layers.

  The lugs of the branches are then arranged or profiled with respect to the corresponding associated recess of the layers

  intermediaries so that, under the action of the

  intermediate areas, at least the extreme areas of

  spells are kept out of contact with the radially outer zones of the annular channel The lugs of the branches can then be arranged in such a way that, during a loading of the intermediate layers, these

  the last ones are drawn by the slightly radially

  In this way, at least one of the extreme turns of the springs does not come into contact with the shell-like bodies, which are also spaced apart from the wall of the annular channel. constitute the annular channel and can thus move elastically freely In this respect, it may be advantageous that the recesses in the intermediate layers have a circular ring-shaped section and that the lugs of the branches have zones adapted at least to the recesses. These areas may for example be produced

  by impression exerted by the lugs which have undergone

  lable a punching The recesses of the intermediate layers

  can considering the axial direction of the springs -

  have a conical or spherical shape and constitute blind holes. According to another particularity of the invention,

  it is possible to arrange radially inside the annular canal

  At least one other group of springs of the damping system may be advantageous for many applications. This other group of springs may be arranged between the flywheel elements in parallel with the

  first group of springs placed in the annular channel.

  The distribution of the different springs of the first and the second group between the two flywheel elements can then be carried out in such a way that at least some springs of the two groups come into action in a staggered manner, that is to say with an offset angular, and / or that at least some springs of at least one group intervene in

  staggered way, that is to say with an angular shift.

  According to another embodiment of the invention,

  vention, the first group of springs placed in the canal

  ring and the other group of springs, arranged radially

  further inwards, are placed in series between the flywheel elements The springs arranged in parallel inside these groups can then also form

  different stages that come into action with

  lar. The coupling of the two groups of springs at least provided, which are arranged between the flywheel elements, can be established in a simple manner using a flange

  which has corresponding recesses for the different

  These recesses can advantageously be

  made in such a way that the flange

  pure radially outer, separated from each other in a directiolỉrference by radial branches and in which are received the springs of the first group, and windows placed radially further in and in which are arranged the springs of the other group Cutouts and windows can

  then be arranged considering a circumferential direction

  -competitive. relative to each other so that each time a window is placed radially inside a cutout The cutouts and the windows can then have in a circumferential direction the angular diisions at least approximately equal. In order to obtain as great an angle of rotation between the two flywheel elements as possible, it may be advantageous if the first and / or the other group of springs each comprise at most four accumulators.

energy.

  For the arrangement and the operating mode of the device, it may be particularly advantageous if, radially inside the annular channel, the housing halves or the shell-shaped bodies, such as profiled sheet metal parts, comprise zones directed towards each other and which constitute a passage for the flange The zones directed towards one another can then define circular ring-shaped surfaces, which

  delimit a passage or gap in the form of a circular ring

  In order to obtain a very large damping by means of the viscous agent housed in the annular channel, the width of the aforementioned passage may be at least approximately equal to the thickness.

  For many applications, however, it can

  It should be advantageous if the axial spacing between the zones directed toward each other is greater than 0.1 mm to 2 mm.

  the thickness of the areas of the flange engaged in said

  Part of the viscous agent lodged in the annular channel can, through the interval thus defined, escape inwards during a relative rotation

  between the two elements of a steering wheel

  the corresponding interval, the amortization effect

  caused by the viscous agent in the

  annular channel can be maintained at the desired value.

  Furthermore, it is possible to arrange the zones directed towards each other, the housing halves and the corresponding areas of the flange relative to each other so that there exists between them an interval varying depending on the relative rotation angle between the flywheel elements, in which case the cross section defined by the gap may decrease as the relative rotation angle increases, so that

  the damping produced by the viscous agent is increased.

  For this purpose, the flange may comprise oriented ramps

  in a circumferential direction at least on one side and

  clinched upwardly in an axial direction, said ramps cooperating with matching contoured ramps on the housing area facing that side,

  so that when the ramps and ramps

  are displaced relative to each other, the

  passage section of the viscous agent is reduced.

  For the mounting of the device, it may be particularly advantageous that the other group of springs is arranged radially inside the passageway formed for the flange between the zones, directed towards each other, of the housing halves To receive this group of springs, the half of the housing or shell-shaped bodies

  may have axial cavities For the functioning of

  the device, it may be in this respect particularly

  Advantageously, the axial cavities interconnect the passage for the flange and the annular channel. For correct guidance of the energy accumulators of the other inner group of springs, it may be advantageous if

  the cells are adapted, at least in a radial zone.

  outside the area, at the edge of the section of these accumu-

  The gap or passage for the flange which is provided between the annular channel and the cells

  can be practically closed For this purpose, the flange

  carries a ring-shaped zone, which extends

  at least partially radially in this range.

  Advantageously, this ring-shaped zone

  circular flange can be formed in the essen-

  by branches extending in a circumferential direction

  radially between the outer springs and the inner springs, said branches interconnecting the support zones of the springs on the flange, as

radial arms.

  To facilitate assembly of the device, the springs of the other group may be pre-curved at least approximately in correspondence with the radius of the circle on which they are arranged.

  long springs In addition, the pre-incur-

  of the outer group and / or inner group springs has the advantage that they are practically

  free from bending moments in the installation condition

* lation and when the device is not requested.

  It may be advantageous for the springs of the other group to be guided radially outwards by the zones defining the windows of the flange so that these springs rest, when the device is in rotation and is biased, mainly against the radially outward contours. the windows of the flange, thus being guided substantially only in an axial direction by the cavities formed in the housing parts, which means that the springs slide with a minimum force of application along the wall delimiting the cells D Advantageously, the outer contours of the windows may be constituted by limbs of the flange lying between the outer springs and the inner springs and oriented in a circumferential direction. To prevent the ends of the springs from being applied against the casing, the different windows or well the branches can be slightly radially inwardly at one end so that the biased ends of the springs are held radially recessed from the radially outer regions

  cells or the annular channel by the flange.

  For many applications, however, it may also be advantageous if the inner springs bear radially, at least under the effect of the forces

  centrifugal, against the surfaces delimiting the cells.

  This can be advantageous in the case of springs which

  in action only after a rotation angle relative to

  In addition, it may be advantageous for the operation of the device that the windows of the flange receiving the inner springs are profiled so that they constitute

  pins oriented in a circumferential direction, which

  directly in the ends of the springs or in a recess of an intermediate layer which is placed between a spring end and the corresponding biasing zone of the flange The lugs may in this respect be arranged relative to the ends of the springs or on the intermediate layers so that they maintain radially inward at least the end zones of the springs so that they remain, during their stress, out of contact with the radially outer areas of the cells and / or the branches of the flange which surrounds them thus also obtains the advantages already described with regard to

  the lugs formed on the branches of the flange.

  For the manufacture of the device, it may be particularly advantageous that the receiving cells of the other group of springs have an annular shape, that is to say that they extend over the entire periphery of the device and that the support zones of the energy accumulators in a circumferential direction are constituted

  by stop elements disposed in the cells.

  Such abutment elements may be constituted by individual elements, such as those described in relation to the abutment members provided in the annular channel. It may be particularly advantageous if the abutment elements are constituted by rivets of form whose zones of stress of energy accumulators are flat or flattened.

  For the arrangement and operation of the

  However, it may be advantageous if the springs of the inner group are housed in windows of two discs which are in a rotating connection with the other steering wheel element.

  which can be connected to the transmission line, and which receives

  axially between them a flange coupling in series the group of radially outer springs and the group of

radially inner spring.

  According to another feature of the invention, it may be particularly advantageous for the operation and assembly of the device that one of the flywheel elements comprises one of the components having a certain profile, an axially interlocking connection and that the Another flywheel element comprises the other reverse profile component of the interlocking connection ensuring the rotational coupling of the two flywheel elements. Such interlocking connection can be advantageous in the case of a device where the groups of springs of the damping system are received in a chamber which can be filled at least in part with a viscous or pasty agent, which is essentially formed by the components of the steering wheel element which can be connected to the engine while the system exit

  cushioning component is a component in the form of a flange

  carries profiled areas engageable with counter-profiled areas provided on the other flywheel member, and furthermore one of the flywheel members carries a sealing member which, upon nesting of the two members flywheel, is sealingly applied against one surface of the other flywheel element. Such a structure allows an initial assembly in the form of two

  sets of which one placed on the primary side can be accom-

  with the engine while the other placed on the secondary side

  can be coupled with the transmission line

via a clutch.

  It may be advantageous that the flange-shaped outlet part of the damping system can be

  connected in a rotating way, without however being blocked axially

  with the other flywheel element through the interlocking connection profile zones With a

  structure of this kind, the flange may be freely

  placed in an axial direction so as not to be blocked

  between the two steering wheel elements when assembling the

  This will result in incorrect loading of the components of the device and in establishing, for relatively small angles of rotation, a large undesirable friction hysteresis, for example during idling of the engine. It may be particularly advantageous if the flange-shaped outlet part of the damping system is mounted axially floating between the two housing halves or the shell-like bodies of the mating flywheel element

with the engine.

  A particularly advantageous arrangement of the device can be obtained by ensuring that the seal established by the assembly of the two flywheel elements seals or closes the chamber, at least partially filled with viscous agent, with respect to at an annular gap disposed axially between the two flywheel elements which can rotate relative to one another and which can be open outwards In this respect, it may be advantageous for the counter-profile wheels to be arranged on the outer periphery of a ring-shaped component which is connected to the other element

steering wheel.

  The sealing element sealing the chamber advantageously comprises at least one annular disk-shaped sealing part. It may be advantageous for the annular disk-shaped sealing part to have an axial flexibility so that , after the interlocking of the steering wheel elements, this part

  may be elastically deformed for the purpose of

  such a seal of water.

  may be carried by the steering wheel element

  be coupled to the engine so that, after the

  parts of the steering wheel, it applies with a pre-

  stress against a bearing surface of the other element

steering wheel.

  To facilitate the mounting of the device, it may be advantageous for the internal diameter of the element

  sealing the chamber in the direction of

  the annular channel is larger than the diameter

  outside of the counter-profile areas of the socket connection.

  In this way, the sealing element may, in the case of

  appearance of the device, to be guided axially through the

  the counter-profile areas, which is particularly

  advantageously when the flange-shaped outlet part of the damping system has a central recess whose peripheral contour delimits the zones

  with the profile of the interlocking connection and when the

  in the form of an annular disc, having the counter-profiled zones on its outer periphery, is fixed axially on a front surface of the other steering wheel element which is directed towards the steering wheel element

side of the engine.

  It is possible to obtain a tight seal

  the recess of the chamber and a simplified mounting of the device when the sealing member bears axially by its radially outer marginal zone against a radial wall of one of the flywheel elements, which is constituted by the housing half which is adjacent to the interval

  radial ring between the two steering wheel elements.

  In this respect, the radially outer marginal area of the sealing element may be axially fixed to the

  radial wall For the operation of the watertight element

  However, it can be advantageous for the latter to be clamped axially on its outer marginal zone. Such clamping, which can be axially elastic, allows the sealing element to pivot around the clamping zone in a manner similar to a Belleville washer The application surface of the sealing element which is provided on the other flywheel element can be created in a simple manner by a circular ring-shaped component, which is clamped axially between the surface front end of the other flywheel element and the component comprising the counter-profile zones and which extends radially outwards further than the counter-profile zones.

  circular ring shape can then be moved radial-

  outward towards the component provided with the

counter-profile areas.

  For many applications, it can be advantageous for the damping system acting between the two flywheel elements to comprise at least one friction device. This friction device can act in the totality of the relative angle of rotation between the two elements of the wheel. flying or it can act only within a certain range of this relative angle of rotation.

  In view of this, it may be advantageous for the friction device to

  The energy accumulator can then be arranged in such a way that the moment exerted by the friction disk is sufficient. , at least over a portion of its compression stroke, to overcome the frictional moment of the friction disk so that

  this one is retracted, at least in part.

  In addition, it may be advantageous for the

  friction positive provided between the flywheel elements is provided with a game in the circumferential direction, which means that there is a clearance between the stops of the friction disk of the friction device and the associated abutments associated with it , the entry into action of the friction device occurs

  following the activation of the energy accumulator.

  To obtain a moment of friction

  as long as possible throughout the service life of the equipment, the device can be

  of friction is arranged in the chamber for

  which is formed by the crankcase halves or by the

body shaped shells.

  For other applications, however, it may also be advantageous to have the outside of the volume or annular channel filled at least partially

  of viscous agent additionally a device for amorphous

  dry rubbing action acting between the two

steering wheel elements.

  Although, for many applications, it may be advantageous for the friction damping device to be arranged in parallel with the springs of the damping system, it may be particularly advisable for other applications to provide between the flywheel elements at the same time. less a damping device

  by friction which is placed in series with the springs.

  The damping action of the friction device and the friction damping device can then be changed in the relative rotation angle, in which case the damping action can increase as

the angle of rotation increases.

  For the operation and assembly of the

  it may be advantageous for depreciation by

  friction and / or viscous damping acting in

  to the inner spring group is substantially

  smaller than the viscous damping and / or the damping

  The external springs can be provided at their ends with cups whose external contour corresponds at least approximately to the contour of the annular channel, so that a large damping occurs. The internal springs, at least those of the first stage, are mounted without cups so as to obtain in the first stage a low grease discharge and consequently also a low damping. The springs of the inner group which are assembled with play can, with a view to optimizing

  damping, be mounted with or without cups.

  In addition, the viscous damping associated with the external group

  The inner annular channel may be advantageous if the outer annular channel is completely filled with acupuncture and the inner cells are only partially filled.

  viscous agent The large damping effect occurs

  the compression of the outer springs therefore begins as soon as the springs begin to be stressed. The damping associated with the inner group of

  However, the springs remain weak because the springs

  only partially in the viscous agent.

  For the operation and assembly of the

  It may be particularly advantageous if the crankcase half is directed towards the engine or the body.

  shaped shell placed on the side of the radial door motor-

  inside an axial appendage which is oriented towards the steering wheel element which can be coupled to

  the transmission line and carrying a bearing

  the two flywheel elements so that they can rotate relative to each other. The flywheel element which can be coupled with the transmission line can

  have an axial recess into which axial

  In this respect, it is advantageous for this recess to form a seat for receiving the outer ring.

of the bearing.

  For the assembly of the device, it is particularly

  advantageously, that before the assembly of the two

  wheel bearing, the bearing is held together by means of shapes on the steering wheel element which can be coupled to the transmission line and that, during assembly, this

  bearing is fitted on a seat of the axial appendage.

  To obtain a characteristic curve of elastic

  of at least a few springs of a group of springs or a damper may be shorter than the arc portion of

  circle located between the stops cooperating with them.

  Other features and advantages of the

  will be highlighted, in the following description

  given by way of non-limiting example, with reference to the appended drawings, in which:

  FIG. 1 represents a section view of a device

  FIG. 2 shows the device in an elevational view made in correspondence with arrow II of FIG. 1, with portions broken away,

  Figure 3 is a sectional view of another

  3 shows on an enlarged scale the detail designated by X "in FIG. 6; FIG. 4 represents the device of FIG. 6 in elevational view taken in the direction of arrow IV, Figure 5 is a half-section of an alternative embodiment of a device according to the invention, Figure 6 is a partial sectional view taken along the line VI-VI of FIG. Figure 7 is a sectional view taken along the line VII-VII of Figure 6, showing components that are only visible in Figure 5; Figure 8 shows details of a device in accordance with Figure 5; which can be used, for example, in the embodiments of FIGS. 1 to 7, FIGS. 9 and 10 show other sections

  devices according to the invention.

  The torque transmission device 1, represented

  1, 1a and 2 and serving to compensate for angular jerks, comprises a flywheel 2, which is divided into two flywheel elements 3 and 4 The flywheel element 3 is fixed on a crankshaft 5 of a internal combustion engine, not shown in detail, by means of fixing bolts 6 On the flywheel element 4 is fixed a friction clutch 7 which can be controlled Between the pressure plate 8 of the friction clutch 7 and the flywheel element 4, there is provided a clutch disk 9, which is mounted on the input shaft 10 of a gearbox, not shown in detail The pressure plate 8 of the friction clutch 7 is actuated in the direction of the flywheel element 4 by means of a rotating spring-spring 12

  on the clutch cover 11 By actuating the clutch cover

  friction clutch 7, the flywheel element 4, and consequently

  also flywheel 2 or the internal combustion engine, can be coupled with the shaft 10 of the box

  of gears and be disconnected from this shaft

  steering wheel 3 and the flywheel element 4, there is provided a first damper 13 radially outside and a

  second radially inner damper 14 arranged in

  the first one, the two dampers allowing a

  relative rotation between the two flywheel elements 3 and 4.

  Both steering wheel elements 3 and 4 are mounted

  through a landing 15 so as to be able to

  to one another, the bearing

  The outer ring 17 of the bearing 16 is mounted in a recess 18 of the flywheel member 4 while the inner ring 19 of the bearing 16 is mounted on a trunnion. central cylinder 20 of the flywheel element 3, which is oriented axially from the crankshaft 5 and which

is engaged in the recess 18.

  The inner ring 19 of the bearing is fitted on the pin 20 and is held between a shoulder 21 of the pin 20 or the flywheel member 3 and a safety disc 22, which is fixed by means of rivets 22a on the side

front of the pin 20.

  The bearing 16 is locked axially relative to the flywheel element 4, being tight, with interposition

  two rings 23, 24 with an L-shaped cross-section, axially

  between a shoulder 25 of the flywheel element 4 and an annular disc 27, rigidly secured via

  rivets 26 on the second steering wheel element 4.

  The two rings 23, 24 form an insulation

  which interrupts, or at least reduces, the trans-

  heat mission between the friction surface 70 of the element

  steering wheel 4, cooperating with the clutch disc 9, and

the bearing 16.

  The wings 23a, 24a, directed radially towards

  inside, rings 23, 24 extend in part radially

  above the inner bearing ring 19 and

  axially against it, so that they serve

  simultaneously wind seal for the bearing 16.

  To ensure proper sealing of the bearing 16, the wings 23a, 24a radially oriented are each biased axially towards the end faces of the inner race ring 19 by a force accumulator.

  having in the form of an elastic disk 28, 29.

  The flywheel element 3 constitutes a housing which delimits an annular chamber 30 in which the dampers 13, 14 are housed. The steering wheel element 3

  comprising the annular chamber 30 is composed of

  two housing parts 31, 32, which are interconnected, radially outwardly, with the aid of

  bolts 33 The bolts 33 are arranged in a radial area

  the front surfaces or joining surfaces 34, 35, through which the two housing halves 31, 32 are applied against one another. The joining surfaces 34, 35 are located radially outwardly. of the first damper 13 To seal the annular chamber 30 with respect to the outside, it

  there is provided a sealing ring 36 which is axially arranged

  between the two joining surfaces 34, 35 and

  In order to receive the sealing ring 36, the casing portion 31 has an axial annular groove 37. For precise positioning of the two housing parts 31, 32 during assembly, it is furthermore possible to provide cylindrical pins 38, which engage, radially outside the sealing ring 36, in holes formed in axial coincidence in the two parts

of housing 31, 32.

  The housing portion 31 directed towards the motor has on its outer periphery a shoulder 39 on

  which is fitted with a starter gear ring 40.

  The two housing parts 31, 32 may be made of cast iron. In the case where it is desirable to have a low moment of inertia for the first flywheel element 3, at least one of the housing parts 31, 32 may be fabricated

  made of lightweight metal alloy, such as an aluminum alloy.

  Such lightweight metal moldings have the advantage that they can be manufactured by a die casting or compression process and can be used without

  involve major finishing operations.

  The two dampers 13, 14 comprise a portion

  a common outlet in the form of a flange-

  radial 41, which is arranged axially between the two halves 31, 32 of the casing The flange 41 is connected without the possibility of relative rotation, as shown in particular in Figure 2, by its radially inner regions with the annular disk-shaped portion 27 by means of an axially interlocking connection 42, this part 27 being fixed by means of the rivets 26 on the front side of the axial appendage 43, oriented towards the crankshaft, of the flywheel element 4. precise radial positioning during assembly, there is provided a centering seat 43a between the annular disc-shaped portion 27 and

the axial appendix 43.

  The flange 41 has on its outer periphery

  radial branches 44 which form the biasing zones of the energy accumulators, in the form of helical springs 45, of the outer damper 13 Radial inside, considering a circumferential direction of the cutouts 46 existing between the branches 44 or helical springs 45, the flange 41 has windows 47 curved profile in

  which the energy accumulators are received,

  felt in the form of helical springs 48, the amorphous

  Inner weave 14 Radially between the cutouts 46 and the windows 47, the flange 41 form tabs or tongues 49 oriented in a circumferential direction and which interconnect the radial branches 44 or the radial zones 50 of the flange 41 which are situated in a groove. circumferential direction between windows 47 Zones

  50 are the loading zones of the flange.

  than 41 for coil springs 48,

  The annular chamber 30 constitutes

  externally a housing 51 in the form of an annular channel or torus, into which radially penetrate the

branches 44 of the flange 41.

  The housing 51 in the form of an annular channel

  the energy accumulators 45 consist essentially of circumferentially extending axial recesses 52, 53 which are arranged in the radial zones of the housing parts 31, 32 and into which the zones axially penetrate. energy accumulators 45 which protrude from each side of the flange 41 Radially towards the inside

  interior, the housing 51 in the form of annular channel is closed by the tabs 49 of the flange 41, apart from a small

interval 54.

  As shown in Figure 1, the axial recesses 52, 53 are profiled in cross-section so that their curved shapes are adapted at least approximately to the periphery of the cross-section of the energy accumulators 45. The outer zones of the recesses 52, 53 may so

  form for the energy accumulators 45 zones of application

  or against which the energy accumulators 45 can rest radially, at least under the action of the centrifugal forces By the adaptation of the zones

  of support, constituted by the recesses 52, 53, at the outer circumference

  energy accumulators 45, it is possible to

  to substantially reduce the wear that occurs as a result of the friction of the turns of the energy accumulators 45 against the delimiting surfaces of the recesses 52, 53 because the surface

  between the springs 45 and the recesses 52, 53 is

  For the stressing of the energy accumulators 45, there is provided on each side of the branches 44, in the recesses 52, 53, circumferential ends 55, 55 a which constitute, in a circumferential direction, zones of In the exemplary embodiment shown, the circumferential stops 55, 55 a have the following:

  considering in a circumferential direction the

  The circumferential stops 55, 55 a consist of parts 56, 57 adapted to the recesses 52, 53 and are fixed rigidly to

  means of rivets 58 on the housing parts 31, 32.

  The end zones, considered in a circumferential direction, circumferential stops 55, 55 a are flattened in

  for better solicitation of energy accumulators.

45.

  Between the branches 44 and the ends, turn

  spring springs 45, spring cups 59 are provided (see FIG. 2), the contour of which is adapted.

  at the cross-section of the housing 51 in the form of an annular channel

lar.

  Radially inside the annular channel housing 51, the casing halves 31, 32 have zones 60, 61 which are directed towards each other, which create ring-shaped surfaces and between which exists a passage 62 in the form of a circular ring

for the flask 41.

  In the embodiment of Figures 1 and 2, the width of this passage 62 in the form of a circular ring is slightly greater than that of the areas of the flange 41 which

  are engaged in it so that there is an inter-

  at least 54 on one side of the flange 41.

  Radially inside the circular ring-shaped passage 62, the housing parts or halves 31, 32 have other axial recesses 63, 64 in which the inner coil springs areas 48 protrude

  on each side of the flange 41 penetrate at least partially.

  As shown in FIG. 1, the axial recesses 63, 64 have a profiled cross-section such that their curved shapes are adapted, at least in a radially outer zone, around the cross-section of the helical springs 48 so that the springs 48 are maintained or guided, at least in an axial direction,

by the recesses 63, 64.

  As well as the outer recesses 52, 53, the inner recesses 63, 64 also extend over the entire periphery of the device. This is advantageous because, for example, the pre-molded recesses 52, 53 and 63, 64 can

  be machined by a turning operation.

  mention of energy accumulators or coil springs

  48, it is provided in the troughs 63, 64 stops

  circumferences 65, 66, which create in a circumferential direction

  conferring support zones for helical springs

  These circumferential stops 65, 66 are arranged in a manner

  similar to the peripheral stops 55, 55a and they are also fixed by riveting on the parts 31, 32 of the housing The circumferential stops 65, 66 are constituted by parts adapted to the recesses 63, 64 and they are fixed rigidly via of rivets 67 on the housing parts 31, 32 As shown in Figure 2, the stops 65, 66 provided on either side of the radial zones

  flange 41 have considering a circumferential direction

  a smaller angular size than the zones

  radial journals 50 which urge helical springs 48.

  The tabs or tabs 49 of the flange 41 are sized relative to the inner recesses 63, 64 of

  such that the coil springs 48 rest

  dialement against the tabs 49 at least under the action

centrifugal force.

  This is advantageous because the flange may be made of steel, which is at least surface hardened so as to reduce wear on the radial bearing areas of the springs 48 Another advantage of the radial support of the springs 48 against the tongues 49 is that,

  until the springs 48 are applied against the circumferential stops.

  65, 66, these springs 48 can rotate with the flange 41 without a significant friction on the housing parts 31, 32 under the effect of the centrifugal force acting on the springs A friction of this

  kind is undesirable in many cases because it has a

  disturbing fluence on the characteristic of the shock absorber

outside 13.

  As shown in Figure 2, it is expected, considering the periphery of the device 1, respectively

  three springs 45 and 48, the radially outer springs

  The radially inner springs 48 extend at least approximately at the same angle as the outer springs 45. In this case, a spring 48 extends at least approximately 100 times. degrees The outer springs 45 thus extend about 91%

  periphery of the device while the inner springs

  The trusses 48 extend over approximately 83% of the periphery.

  In the unmounted condition, the springs 45

  and / or the springs 48 can by considering a direction

  axially be straight, which means that,

  during assembly, these springs must be curved

  correspond to the shape of the hollows receiving them, or else

* during also the springs 45 and / or the springs 48 may already have a curvature corresponding to the shape

  receiving valleys using pre-incurve springs

  45, 48, it is possible to reduce

  in the springs during their compression and, in

Besides, editing is easy.

  In the annular chamber 30, there is provided a viscous agent or a lubricant, such as for example a silicone oil or a grease. The level of the viscous agent or lubricant can then when the device 1 turns to reach at least the zone In the embodiment shown, it is advantageous for this level to reach at least the outer zones of the turns of the inner coil springs 48 so that lubrication occurs. reducing the wear at least between said turns and the zones supporting them radially, namely in the case considered the tabs 49 of the flange 41 In the device shown, it is advantageous for the filling in viscous agent or lubricant to reach

  approximately the axis of the inner coil springs 48.

  Thanks to the combination of the annular chamber 30, which contains a viscous agent or a lubricant, with the flywheel element 3 connected to the engine and thanks to the spatial separation with respect to the flywheel element 4 carrying the friction clutch 7, to a large extent excludes an influence of the heat produced by the clutch

  friction on the viscous agent or the lubricant.

  In addition, it is provided between the annular chamber 30, or the housing part 32, and the element of

  steering wheel 4, an annular channel or annular gap 68 or-

  green towards the outside and which further enhances the effect of

  The ventilation ducts 69 are arranged radially inside the friction surface 70 of the cooling element.

  steering wheel 4 for the clutch plate 9.

  As shown in particular in Figure 2, the flange 41 has a central recess 71 whose contour constitutes radial zones with profile 72, which engage with

  counter-profile areas 73, which are provided on the

  outer surface of Part 27 in the form of an annular disc

  which is connected to the steering wheel element 4

  profile 72 and the counter-profile areas 73 forming the link

  its interlocking axial 42 allow a correct orientation

  flange 41 between the two halves 31, 32 of the housing so that the gap 54 existing between the passage 62 in the form of circular ring and the flange 41 can be very small Also, the interlocking connection 42 allows an enlargement axial tolerances between different

  stop or support surfaces of the components.

  In order to seal the annular chamber 30, there is provided a seal 74 between the radially inner zone of the housing portion 32 and the annular disk 27 or the axial appendage 43 of the Flywheel element 4 The seal 74 comprises a circular ring-shaped disc 75, which is supported by its radially inner zone against a shoulder 76 formed on the axial appendix 43 and by its outer zone against a surface 77 , which is located on a radially in-

  inner portion of the annular housing portion 32.

  The disk 75 in the form of a circular ring is deformable axially in a manner similar to a disk spring or

  Belleville washer The disc 75 in the shape of a circular ring

  the wheel is pushed axially against the shoulder 76 and against the surface 77 by an elastic disc 78, which is tight

  axially between the disc 75 and the flange 41.

  of the elastic disc 78, also the flange 41 is

  pushed against the surface 60, so that only

  on one side of the flange 41 a gap 54 between the housing 51 in the form of annular channel and the zones of the

  chamber 30 which are located radially further towards the

  As shown in Figure 1, the seal

  74 seals the chamber 30 with respect to the

  annular tervalle 68 existing between the two flywheel elements 3 and 4 The inner diameter of the disc 75 sealing the chamber 30 relative to the annular gap 68 is greater than the outer diameter of the

  counter-profile parts 73 of the interlocking connection 42.

  The interlocking connection 42 and the seal 74 allow a particularly simple assembly of the torque transmission device 1, in that in particular the two flywheel elements 3 and 4 are pre-mounted and are then axially connected to one another. with

  the other by axial interlocking and securing the safety disk.

  22 to the front side of the pin 20 For this purpose, initially the seal 74 is pre-mounted on the flywheel member 3 and the bearing 16 is blocked by conjugation of shapes on the flywheel member 4. the assembly of the two flywheel elements 3 and 4, the inner ring 19 of the bearing is fitted on the seat 20a of the axial appendage 20 of the housing portion 31 and the

  counter-profiles 73 come into contact with the

  In addition, during the engagement of the two flywheel elements 3 and 4 with each other, the radially

  the inner ring of the sealing disk 75

  against the corresponding sealing surface

  killed by the shoulder 76 so that the disc of water

  Choke 75 pivots under the effect of the force exerted by the elastic disc 78 and is applied with prestress against the shoulder 76 The final axial locking of the two flywheel elements 3 and 4 relative to each other is carried out, as already stated, by fixing the

disc 22 on the journal 20.

  To reduce wear in the area of contact between the turns of the springs 45 and 48 and the recesses 52, 53

  and 63, 64 which are mutually associated with them, it is pos-

  to give at least in these contact areas a

  greater hardness on the surfaces of parts 31, 32 delimits

  Both of these indentations can be achieved by, for example, treating these contact areas by induction quenching, case hardening, laser quenching.

  or by flame-quenching In the case of very heavy

  However, it may be advantageous if the portions 31, 32 delimiting the recesses comprise, at least in the abovementioned contact areas, a coating which reduces the frictional wear. Such a coating may for example be formed by chemical nickel plating, chromium plating or deposition of plastic or molybdenum deposited coating

  may further be rectified in such a way as to

  to maintain a better surface quality of the recesses against which the turns of the springs rub Such surfacing can be achieved for example by a grinding process

or by lathe machining.

  The mode of operation will be described below.

  the device in accordance with Figures 1 and 2.

  When rotating the flywheel element 4 relative to the flywheel element 3 from the position

  resting position shown in Figure 2, the flange 41 is

  dragged through the interlocking connection 42 such that initially the outer springs 45 are compressed between the circumferential stops Es 55, 55a and the radial branches 44 After a relative rotation of the angle 79 in a direction of rotation or angle 80 in the other direction of rotation, the circumferential stops 65, 66 are applied against the inner springs 48 so that, in another Relative rotation between the two flywheel elements 3 and 4 , the springs 48 are

  tablets in addition to springs 45

  mune springs 45 and 48 occurs until the inner springs 48 are completely crushed, which

  limit the relative rotation between the two elements of

  3 and 4 In the exemplary embodiment shown,

  the maximum angle of rotation, from the position

  rest, shown in Figure 2, is of one order

  47 degrees in both directions of rotation.

  During a relative rotation between the two elements of

  3 and 4, there is a friction damping

  external springs 45 against the surfaces of the recesses 52, 53 and by friction of the flange 41 against the surface 60 There is also a friction damping between the radially inner springs 48 and their radial bearing zones.

  occurring between the springs 45, 48 and their zones ra-

  Supporting dials are a function of the speed of rotation, this damping increasing as the rotational speed increases. In addition, damping is produced by turbulence or backflow of the viscous or pasty agent contained in the annular chamber 30. the viscous agent in the substantially closed annular channel housing 51 produces a hydraulic or viscous damping because the spring cups 59 act as

  pistons in this annular channel-shaped housing.

  In case of compression of the outer springs 45, the

  spring shovels 45 urged by the branches 44, are moved towards the cups leaning against

  the circumferential stops 55, 55 has the result that

  in the springs is pushed back into the

  felt through the interval 54, which acts

  Similar to a choke Another part of the viscous agent is forced back between the spring cups

  59 and the walls of the housing 51 in the form of an annular channel.

  The viscous agent initially discharged inwards is distributed again, under the effect of the centrifugal force acting on it, uniformly on the periphery. During the expansion of the outer springs 45, the viscous agent lying on the side of the cups 59 which is opposed to the springs 45 is compressed in a similar manner against the cups and is forced through the gap 54 so as to refill the springs 45 under the effect of the centrifugal force acting on it. produced by the viscous agent is a function of the centrifugal force

  acting on that agent, which also means that the

  Increases when the rotational speed increases.

  The areas of the radially inner springs 48 which penetrate the viscous agent also produce

  viscous or hydraulic damping by turbulence

  lence. By performing unwinding or axial cutting in at least some cups and by a corresponding dimensioning of the interval 54 or the

  outer circumference of the cups, it is possible to

  the damping produced by the viscous agent or

  to adapt it to each case of application.

  viscous or hydraulic structure can be adapted to

  seeing only some of the springs 45 of cups 59.

  Also, the cups can be placed between the ends

  at least one inner spring 48 and

dials 50 of the flange 41.

  The device shown in Figures 3 and 4 comprises two flywheel elements 3 and 4, which are mounted, as in the device of Figures 1 and 2, so as to be rotatable relative to each other via of a bearing 16 The disk 122 ensuring the axial attachment of the two flywheel elements is fixed on the front side of the axial appendix 120 by means of rivets 122 a The assembly of the two flywheel elements 3 and 4 is carried out in a manner similar to that described with reference to Figures 1 and 2 This means that the bearing 16 is first pre-mounted on the flywheel element 4 and that, when assembling the two elements 3 and 4, it is fitted on the seat 120a of the axial appendix 120 In addition, before the assembly of the two flywheel elements 3 and 4, a seal 174 is pre-mounted on the element 3 of the flywheel to be installed on the motor side and there is provided an interlocking connection 142 between the flange 141, which constitutes the output portion of the two dampers 13, 14, arranged in parallel, and the disk-shaped component 127, which is fixed on the flywheel element 4 by means of rivets 126 The two Housing parts 131, 132 delimiting the annular-shaped chamber 130 are formed as moldings. The housing portion 132 has on its periphery an axial cylindrical appendage 132a, the inner peripheral surface 135 of which serves to center the housing. part of crankcase

  132 on an outer peripheral surface 134 of the

  The axial fastening of the two moving parts

  The casing portion 132 carries a starter ring gear 140, which axially clings in part to the casing portion 132, 132 of the casing is provided via radial pins 138 which are provided in an area of the centering surfaces 134, 135. the pins 138 so that

  these can not float radially.

  The interlocking connection 142 is con-

  formed by radial branches 172 formed on the periphery

  inner flange 141 and clinging between radial projections 173 formed on the outer periphery

  of the annular disk-shaped component 127.

  As shown in particular in Figure 3a, the seal 174, provided between the radially inner zone of the housing portion 132 and the annular disk-shaped component 127 or the axial appendix 143 of the steering wheel element 4 comprises an axially flexible disk 75 in the form of a circular ring which is supported by its radially inner zone against an annular component 176 fixed on the axial appendage 143 and which is fixed axially by its radially outer zone against

  a radially inner zone of the housing portion 132.

  The axially deformable sealing disc 175, in a manner similar to a disc spring or Belleville washer, bears on its radially outer and radially inner surfaces a coating 175a, 175b, as a coating

  plastic material, which is deposited for example by pulverulent

  These coatings 175a, 175b must have a low coefficient of friction and a certain

  elastic or plastic deformation The marginal zone ra-

  outer dial of the sealing disk 175 is folded

  in a sealed manner in a support 180 of annular shape.

  The crimping of the outer area of the sealing disc is made such that the sealing disc 175 can be tapered. The zones 180b of the annular support 180, which cling to the outer periphery of the disc 175 are housed in an axial recess or an axial reinforcement 177 which is formed in a radially inner zone of the housing portion 132 for the axial fixing of the outer zone

  of the sealing disk 175, the support 180 of annular shape

  The annular support 180 is provided with folded-away zones 180a which engage radially on the inner edge 132b of the housing portion 132. The annular support 180 for the sealing disk 175 is deformable in the manner of a disk spring. or Belleville washer, a ring support

pivoting.

  The annular shaped component 176, which has a sealing surface cooperating with the sealing disc 175, has a radially inner disk-shaped zone 176a, which is axially clamped between the end surface of the axial appendix 143 and the disk-shaped component 127, as well as an outer zone 176 b in

  form of circular ring against which

  Waterproofing the sealing disc 175 with axial prestressing. The radially outer regions 176b of the annular shaped component 176 are offset back from the radially inner regions 176a, in

  an axial direction, the annular disc-shaped component

  With the counter-profile zones 173 of the interlocking connection 142, as shown in FIG. 3, the seal 174 seals the shaped chamber.

  ring 130 with respect to the annular gap 168

  both between the steering wheel elements 3 and 4.

  To allow axial engagement of the two flywheel elements 3 and 4, the inside diameter of the sealing disc 175 is larger than the outside diameter

  radial projections or counter-profiled areas 173.

  The zones 176 b of the component of the annular formula 176, against which the sealing disk 175 bears axially, extend radially outwards further than the

  counter-profiled areas 173 When fitting the wheel

  16 on the seat 120a, the interlocking connection 142 is established and the sealing disc 175 is axially locked.

  by application against counter-profiled areas 176 b.

  To prevent or reduce wear on the radial bearing areas of the springs 145 in the annular channel-shaped housing 141, a steel strip 181 of high hardness, which extends over the periphery of the housing 151, is provided. in the form of an annular channel and which surrounds

  the springs 145 The steel strip 181 has a cylindrical profile

  drique and she's engaged in a recess 182 that's

  constituted by a radial hollow or a radial recess.

  When the device 101 rotates, the springs 145 become

  against the steel band 181 by means of their turns under the effect of the centrifugal force acting

on them.

  The circumferential stops 155, 155 a for the outer springs 145 and the circumferential stops 166 for the inner springs 148 consist of profiled parts, such as forgings, moldings, which comprise rivets 158, 167 formed of one piece for fixing on the housing part

corresponding 131, 132.

  As shown in Figure 4, the abutments 155, a, disposed on each side of a branch 144 of the flange

  141, have a larger dimension in the circumferential direction

  as the branches 144; in the exemplary embodiment shown and in the rest position indicated in FIG. 4 for the device, the branches 144 are disposed in the middle with respect to the abutments 155, 155 a, which means that the stops 155, 155 have exceeded the same distance

144 branches on both sides.

  The circumferential stops 165, 166, which are

  arranged on either side of the radial zones 150 of the flange.

  141, also comprise in a circumferential direction a greater dimension than the zones 150 which serve to bias the springs 148. The arrangement of the abutments 165, 166 with respect to the radial zones 150 is however designed so that the circumferential stops 165, 166 on one side of the zones 150 in the rest position of the device 101, while on the other hand, the stops 165, 166 and the radial zones 150 can be placed in coincidence. The abutments 165, 166 with respect to the radial zones 150 are designed such that two abutments 165 or 166 following in a circumferential direction are offset in an opposite angular direction relative to the radial zones 150 of the flange 141 which are associated with them. In this arrangement, the inner springs 148 form two groups of springs, namely the groups 148a and 148b, which enter

in action in a staggered manner.

  The viscous or lubricating agent, such as for example a silicone oil or a grease, which is placed in the annular chamber 130, must fill at least

  the housing 151 in the form of annular channel when the dis-

  positive 101 is in rotation It may however be advantageous

  that the level of the viscous agent or lubricant

  at least the outer zones of the turns of the inner helical springs 148, in which case it may be particularly

  advantage that the filling in viscous agent or in lubricant reaches approximately the axis of

  internal coil springs 148.

  Between the branches 144 or circumferential stops

  155, 155 a and the ends of the springs 145 which are directed towards them, there are provided spring cups 159, whose circumference is adapted to the section of the housing 151 in the form of an annular channel. Thus, as described in FIG. relationship with Figures 1 and 2, it is

  produced a comparatively large depreciation

  the viscous agent in chamber 130

annular shape.

  The spring cups 159 comprise a nipple 159a slightly conical, which penetrates axially into

  the springs 145 the end 159 b of the pin 159 has a

  conical thread in the embodiment shown, but

  it could, however, also have some form of

  With such an arrangement of the spring cups 159, when during operation a sliding of a cup deviates from the end of the spring, this cup is automatically reengaged in the spring when a new biasing of the cup or expansion of the spring, so that the spring or the cup are not damaged An escape cups 159 may then occur when the outer springs 145 are compressed and when the device 101 rotates at a comparatively large rotational speed In this operating condition, the friction between the turns of the springs 145 and the radial bearing areas of the housing halves 131, 132 is sufficiently large that the springs 145 can not relax completely. in

  the case of a sudden and alternating variation of the load.

  Under the effect of the discharge of the viscous agent, caused by the radial branches 144 during the abrupt variation

  alternated with the load, this agent being distributed again

  calf outside under the effect of centrifugal force,

  the cups 159 can not be excluded from the extremes

  springs 145 which do not relax.

  We will now describe the following mode

  operating mode of the device according to Figures 3 and 4.

  When the flywheel element 4 is rotated relative to the flywheel element 3 from the rest position shown in FIG. 2, the flange 141 is driven via the interlocking connection 142 of FIG. so that initially the inner springs 148b are compressed between the circumferential stops I 65, 166 and the radial zones 150. After a relative rotation of the angle 179 in a direction of rotation 190, the radial zones 150 of the flange 141 come apply against the ends of the inner springs 148 a, so that, in the case of additional relative rotation between the two flywheel elements

  3 and 4, the springs 148a and 148b are compressed together.

  After a relative rotation of the angle 179a in one direction of rotation or the angle 190a in the other direction of rotation, the outer springs 145 are biased by the radial branches 144 so that, during a rotation relative additional, the springs are compressed between the circumferential stops 155, 155 a and the radial branches 144 In the embodiment shown, the anal 179 is equal to the angle 179 a and the angle 190 is equal to the anal 190a, so that springs 148a and springs 145 act

  At the same time, we obtain in the example of realization

  tion shown in Figures 3 and 4, a characteristic curve

  The angles 179, 190, 179a, 190a, however, may have only partly the same value or different values, so that it is possible to have at least one characteristic of elasticity. three-stage in both directions of rotation or a characteristic curve of elasticity at least two

  stages in a direction of rotation, and a characteristic curve

  tick of elasticity at least three floors in the other

sense of rotation.

  In addition, the circumferential limit stops 165, 166,

  as shown in phantom lines Figure 4 in 165a, may

  may be offset back from the ends of the springs 148b which are retained in the flange, so that no elastic action occurs in a given angle on either side of the relative zero position of rotation between the two steering wheel elements 3 and

  4 and only intervene, if necessary,

  hydraulically or viscously and / or friction damping.

  The size or characteristic of the amor-

  The hydraulic or viscous flow can be modified by equipping for example only external springs of cups 159 or by not having any cup 159 at one end of at least one spring 145. In addition, at least one of the springs 148a and / or 148 b can be fitted with cups Other factors affecting the viscous or hydraulic damping are the height

  radial filling viscous agent as well as the

  the interval (s) between the flange 141

  and the surfaces 160, 161 of the housing halves 131, 132.

  Hydraulic or viscous damping due to backflow or turbulence of the viscous agent occurs in a manner analogous to that which has been described in

relationship with Figures 1 and 2.

  As shown in Figure 4, it is planned on

  the periphery of the device 101 respectively four res-

  spells 145 and 148, the radially outer springs 145

  each extending at least approximately 78 degrees.

  The radially inner springs 148b extend at least approximately 74 degrees and the springs 148 a at

  less approximately 68 degrees from the periphery.

  Thus, the outer springs 145 extend at least

  approximately 86% of the periphery whereas, on the other hand, the inner springs 148 extend at least

  approximately 79% of the periphery.

  As shown in particular in Figure 4, the

  component 3a of the flywheel element 3 has on its

  outer pheresis radial branches 186 in each

  of which is provided a threaded hole 187 for fixing

  Some of the branches 186 have holes 188 for receiving pins.

  which ensure a precise positioning of the cover of

  clutch on component 3a during assembly.

  The radial branches 186 allow a mode

  easier construction of the steering wheel element 4.

  In addition, thanks to the radial recesses 186 has existing between the radial branches 186, it is possible to ensure better cooling of the component 3 has and the clutch

  mounted on it, because a circulation of air can occur

  between the cover and the recesses

  within the friction surface 4a of the component

  3a, ventilation channels 169 are provided which lead to

  in the radial gap 168 between the two

steering wheel elements 3 and 4.

  The radial branches 186 further allow, for a predetermined mass, to make the component 3 a thicker in the area of the friction surface 4 a so

  to be able to avoid overheating in this zone.

  A modification of the damping produced by the viscous agent may also be obtained by ensuring that the annular channel-shaped housing 151 does not have a constant section at least in zones

  of the longitudinal dimension of at least one

  fate 145, so that in areas of great

  In this case, a lower depreciation

  areas of small section greater damping.

  Although this section variation of the annular channel-shaped housing 151 can be provided in one place

  in some places, it is particularly

  advantageously that such section variations or section enlargements are provided for in

  the ends of uncompressed springs 145.

  Section variations can then be abrupt or

  In this respect, it is particularly

  that the sectional enlargement is provided in the region of the radially inner half of the annular channel-shaped housing. Such enlargement is shown in FIG.

  enlargement 189 is made on the flange 141 which delimits

  moth or radially inwardly close the housing 151 in the form of an annular channel The enlargements can however be created by a corresponding profiling of the recesses 152, 153 delimiting the housing 151 in the form of

annular channel.

  The torque transmission device 201 shown in FIGS. 5 and 6 and serving to compensate for angular jerks comprises a flywheel 202 which is divided into two elements 203, 204 The two flywheel elements 203 and 204 are mounted so as to be able to turn one by

  report to the other through a landing 15.

  The flywheel element 203 constitutes a housing which delimits a chamber 230 of annular shape in which is placed

a damping device 213.

  The flywheel element 203 comprising the annular-shaped chamber 230 essentially consists of two housing parts 231, 232, which are connected one with

  the other radially outside The two parts of car-

  231, 232 are constituted by profiled pieces of

  sheet metal which are assembled with each other on their

  This weld 238 simultaneously seals the annular-shaped chamber 230 radially outwardly. For the welding of the two profiled sheet-metal parts 231, 232, it is advantageous to use a welding process. resistance end or a capacitor discharge welding process, ie a soldering process in which the areas of the two components which are in contact with each other and which are to be assembled are brought together welding by applying to the components of a high current and low voltage alternating current, being heated to the welding temperature and being

subjected to pressure.

* For carrying out such a welding, the two shaped sheet metal parts 231, 232 in the form of shells have frontal areas or junction areas 234, 235 which have a defined extent with respect to the intensity of the current used In the area of these joining surfaces 234, 235, the housing parts 231, 232 are applied axially against one another.

  the other and they are welded together.

  For accurate radial positioning of

  two parts of casing 231, 232 during welding, the part

  231 of the casing comprises radially on the outside a

  annular protrusion 231a, which clings to a superstructure

  centering face 235 formed on the outer periphery of the housing portion 232 For precise positioning in the circumferential direction during welding, axial recesses 265, 266 are provided in the housing parts 231, 232 in these recesses 265 , 266 can engage pins of the welding device, which hold the two housing parts 231, 232 in an angular position

  specifies one in relation to the other in the course of solder.

  Because during the welding of the two co-

  sheet metal pins 231,232, it occurs as a result of the formation of the weld bead some axial movement

  between these shells, it may be advantageous to

  see between these sheet shells axial abutments that occur during welding In Figure 5 it is highlighted in phantom lines such a stop formed

  on the plate shell 232 and designated by 267 By

  With such limiting abutments 267, the intensity of the current used for welding is no longer so dependent, which means that it is also possible to operate with a higher current current because the axial position of the two parts of 231, 232 is determined by the stops 267, and not by the intensity of the current and the axial pressure exerted during the welding on both

housing parts 231, 232.

  The output portion of the shock absorber 213 is

  constituted by a radial flange 241, which is axially arranged

  The flange 241 is secured by its radially inner regions and by means of an axially interlocking connection 242.

  the ring-shaped portion 227, which is itself

  same fixed on the front side of the axial appendix 243, directed towards the housing portion 231 located on the engine side, of the flywheel element 204, via

rivets 226.

  The flange 241 has on its outer periphery

  the radial branches 244 which constitute the zones

  solicitation for energy accumulators, are presented

  both in the form of helical springs 245, the amorphous

weaver 213.

  The two housing parts 231, 232 form radially on the outside a housing 251 in the form of an annular channel or torus, into which the radial branches 244 of the flange 241 penetrate. The housing 251 in the form of an annular channel for the energy accumulators 245 is essentially constituted by imprints or hollow

  252, 253 extending on the periphery, which are

  swung in the housing parts 231, 232 made of sheet metal and in which the areas of the accumulators penetrate

  245 which protrude from each side of the flange 241.

  Radially inwards, the housing 251 in the form of an annular channel is closed off by a zone of annular shape

  249 of the flange 241, apart from a small gap 254.

  As shown in FIG. 5, the axial recesses 252, 253 have a profiled cross-section such that its curved shape is adapted at least approximately

  on the periphery of the cross-section of the accumulators

  3 c yie 245 The outer zones of troughs 252, 253 may

  thus constitute for the accumulators of energy 245

  areas of support or guidance against which

  energy accumulators 245 can rely radially on the

  less under the effect of centrifugal force.

  For the solicitation of the energy accumulators 245, there is provided on both sides of the branches 244 in the recesses 252, 253 of the circumferential stops 255, 255 a In

  the embodiment shown, the circumferential stops

  tials 255, 255 a have in considering a circum-

  the same dimension as the radial branches 244 of the flange 241. As shown in FIG. 6, there are provided between the branches 244 and the ends of the springs 245 which are associated with them intermediate pieces in the form of spring cups 259, whose periphery is adapted to the straight section of housing 251 shaped

annular channel.

  Radially within the annular channel housing 251, the housing halves 231, 232 have zones 260, 261, directed toward each other, forming annular surfaces and between which there is a channel-shaped passage. circular ring 262 for the flange 241. In the embodiment shown in FIGS. 5 and 6, the width of this passage 262 in the form of a circular ring is only slightly greater than that of the zones of the flange 241 engaged in said passage. ,

  so that there is a very small gap 254.

  As shown in Figure 6, it is expected, considering the periphery of the device 201, four

  springs 245 which each extend at least approximately

  72 degrees from the periphery Thus the springs cover at least approximately 90% of the periphery

of the device 201.

  For the reduction of tensions occurring

  in the springs 245 during their compression and for ease of

  In the assembly, the springs 245 are pre-curved at least approximately to the radius of the circle on which they are arranged. In the annular chamber 230, there is provided a viscous agent or a lubricant. The viscous agent must in this respect when the device 201 turns to fill

  at least the housing 251 in the form of an annular channel.

  As shown in Figure 6, flange 241 com-

  carries a central recess 271 whose contour forms radial profile areas 272, which engage with counter-profiled areas 273 which are provided on the outer periphery of the ring-shaped portion 227 which

  is connected to the flywheel element 4 Areas to be counterproduced

  wire 273 are created by radial protrusions which

  In the region of the radial protrusions 273, there are also provided rivets 226 which secure the component 227 to the flywheel element 204. The profiled zones 272 and Counter-profiled areas 273 forming the axially interlocking connection 242 permit proper alignment of the flange 241 between the two housing halves 231, 232 so that the gap 254 between the circular ring-shaped passage 262 and flabby

241 can be very small.

  Also the interlocking connection 242 makes it possible to widen the axial tolerances between the different

  application or support surfaces of the components.

  To seal the annular-shaped chamber 230, there is provided a seal 274 between the radially inner zone of the annular portion.

  casing 232 and the steering wheel element 204

  The gap 274 differs from the seal 174, described in connection with Figure 3a, essentially in that the axially flexible and circular ring-shaped disc 275 is completely covered and is axially radially clamped outside between an annular zone 232a of the housing portion 232 and an annular disk 280 fixed to the housing portion 232

using rivets 232 b.

  The annular zone 232 of the housing portion 232 extends radially inwardly from the outer diameter of the elastic sealing disk 275 so that a radial volume 232c is formed between the zone

  of annular shape 232a and the sealing disc 275.

  In this radial volume 232c, radially open towards the

  the small amounts of viscous agent that may escape between the

  inside of the sealing disk 275 and the surfaces cor-

  seals 276 b and, at speeds of rotation

  tion and under the effect of centrifugal force -

  this viscous agent can again be discharged towards the annular chamber 230 passing between the

  annular zone 232a and the sealing disc 275.

  The contact surfaces between the inner zones of the

  sealing 275 and the corresponding zones of

  276 b are placed in an orientation zone

axial radial volume 232 c.

  On an inner region of the housing portion 232 is formed an axial recess or an axial recess 291, the radially outer circumferential surface of which engages axially on the outer areas of the disc.

sealing 275.

  The housing half 231 turned towards the engine internally carries an axial appendage 220 on which is mounted, in a manner similar to FIG. 1, the bearing 16 allowing relative rotation of the two flywheel elements 203 and 204. The profiled sheet metal part 231 is centered on a seat 201b of Appendix 220 and is supported axially against a radial surface 220c of Appendix 220, which

  is planned following the seat 220 b.

  The connection between the shaped sheet metal part or housing part 231 and the axial appendix 220 can be established by screwing, riveting, welding or fitting. The assembly of the two flywheel elements 203 and 204 is carried out in a manner similar to that described with reference to FIGS. 1 and 2, which means that the bearing 16 is initially pre-mounted on the element

  204 and that the sealing disc 275 is

  In engagement with the bearing 15 on the seat 220a of the appendix 220, the interlocking connection 242 is established and the sealing disc 275 is clamped axially by application against the corresponding sealing zones 276b provided on the flywheel element 204 By fixing the safety disc

  222, which radially covers the inner ring of the wheel

  16, on the front side of the appendix 220, the two flywheel elements 203 and 204 are locked axially relative to each other. The fastening of the disk 222 can be effected by riveting, in a manner analogous to that which is shown in Figure 6 In place of rivets,

  could however also use bolts.

  Hydraulic or viscous damping by means of

  flow or turbulence of the viscous agent is

  in the annular channel housing 251 is produced in a manner similar to that described in FIG.

relationship with Figures 1 and 2.

  To prevent the welding of both parts

  The components which are in contact with these parts, such as in particular the moving components, are welded locally to the housing parts or undergo a modification of the crystalline structure under the effect of localized superheating. electrical insulation is provided between these components and the sheet metal parts 231, 232 of the casing. With regard to the components endangered during the welding process, these include the springs 245 placed in the channel-shaped housing 251. ring, and in addition flange 241 and

cups of springs 259.

  The insulating coating may be provided on the housing parts 231, 232 and / or on the components 245,

  241, 259, 255, 255 a being in contact therewith.

  The insulating coating can then only be deposited

  tically, which simply means in the zones of

  contact between the parts of the housing and the other components.

  The insulation can be advantageously carried out by phosphating certain components. In addition, some components, such as cups

  of springs 259 and the circumferential stops 25 s, 255 a, may

  may be made of a non-conductive material.

  It is particularly advantageous that at least

  the sheet metal parts and / or the flange undergo phospha-

  The springs 245 are advantageously

  lacquered, but they can also be phosphated.

  To isolate the housing parts 231, 232 from the components in contact with them, it is also possible to use ceramic layers, plastic layers or also layers of grease. Such layers can be deposited. especially

on housing parts 231, 232.

  When sheet metal parts 231, 232 have been coated,

  completely killed during the insulation treatment, such as by phosphating, it is advantageous that, in the region of the welding zones as well as in the region of application of the welding current, the insulating layer previously deposited on said zones be removed for example by a mechanical machining process, in order to obtain in these zones a conductivity

correct electric.

  When choosing insulation means, it must be constantly ensured that these means are compatible with the viscous agent introduced into the housing 251.

annular channel shape.

  The use of a phosphate layer as an insulating layer is particularly advantageous because it

  reduces wear and has a self-lubricating effect.

  The housing portion 231 further comprises on the outer periphery a seat 239 on which is engaged a starter toothed crown 240. The starter toothed crown 240 is connected, considering its periphery, to the

  less locally with the housing portion 231 by a

  The latter is advantageous in the case where the housing part 231 is made of sheet metal because, due to the limited thickness of the wall of the housing part 231, the seat 239 does not extend. over the entire width of the ring gear. As further shown in FIG. 5, the engine side housing portion 231 is thicker than

the housing part 232.

  As shown in Figure 7, the circumferential stops

  Figures 255, 255a of Figure 5 may be replaced by profiled portions formed by stamping in the sheet metal parts 231, 232, for example, pocket shaped portions 255c, 255d. These pockets 255c, 255d may advantageously be used for a relative positioning of the two parts 231, 232 of the housing during welding

  Indeed, it is provided on the welding device

  corresponding lies which are adapted to the pockets 255c, 255d.

  These projections can then form electrodes that apply

  the welding current required for the crankcase parts

  231, 232 With the aid of said projections, it is also possible

  to exert on the parts of casing 231, 232 the pressure

  In this respect, it is particularly advantageous for said projections to be arranged in the welding device in such a way that

  that they have a predetermined spacing during the

  so that it can be ensured as well as the two housing parts 231, 232 occupy during and after welding a well-defined axial position relative to each other This is important with regard to the springs 245 placed in the housing 251 in the form of annular channel and in particular with regard to the defined spacing to maintain between the two zones 260, 261 and the flange 241 disposed between them, this spacing having an influence on the hydraulic damping or viscous produced by the device.

  The detail shown in Figure 8 for a dis-

  positive 301 highlights a flask 341 on the periphery

  outside of which radial branches are formed 244.

  By means of the branches 44 can be solicited energy accumulators, in the form of helical springs 345, 345a, as described in connection with the preceding figures The energy accumulators 345, 345a are placed in an annular channel-shaped housing 351 which is constituted by components of

  the flywheel element 303 The spring 345a is urged to

  rightly by the radial branches 344 whereas, against a cup 359 is interposed between the spring

345 and the radial branch 344.

  The branch 344 comprises profiled parts in the form of pins or lugs 344a, 344b

  oriented in a circumferential direction.

  The cup 359 has a recess 359 in which the pin 344 engages. The pin 344a and the recess 359a are arranged and arranged such that at least during a biasing of the spring 345 the cup 359, and through it the end zone of the spring 345, are retained or raised relative to the radially outer regions of the housing annular channel-shaped 351 For this purpose, the radially inner zone of the pin 344a has an inclined inlet ramp 344c which cooperates with a bearing zone 359b of the spring cup 359 Under the effect of the inlet ramp 344c of the pin 344a, the cup of spring 359 is solicited

  or pulled radially inward.

  The lug 344b comprises, radially on the inside, a chamfer 344d, which cooperates with the end turn of the spring 345a and which biases or forces it radially.

towards the inside.

  When using a spring cup 359, it is advantageous for at least the cross-section of the inlet ramp 344c to be adapted to the contour of the recess 359a so that one can also obtain, during a rotation of the spring cup 359, a correct application of the latter against the pin 344 has or against

branch 344.

  Protuberances or pins 344a or 344b may

  should also be provided for advantage

  dials and / or the radial zones of the flange in accordance

in Figures 1-7.

  Such studs 344a, 344b have the advantage that, also at high rotation speeds, at least the end zones, that is to say thus certain turns of the

  coil springs, are maintained radially out-

  non-contact with other components or other areas, so that said spring turns can move elastically freely, i.e.

  produce no friction damping.

  Furthermore, with such lugs 344a, 344b, it can be ensured that, also in rotational speed ranges in which the friction normally generated between the spring turns and their radial bearing surfaces is sigrand that the turns can no longer move elastically, at least the extreme zones of the springs still have elasticity or

  This is particularly advantageous for

  firing oscillations of high frequency and small amplitude

  angular study that occur in said ranges of

rotational speeds.

  In the variant embodiment of a device 401 which is diagrammatically shown in FIG. 9, to ensure the sealing of the annular chamber 430, at least partially filled with a viscous agent, the flange 441 is riveted in a sealed manner directly on an axial appendix 443 of the flywheel member 404, and there is further provided a seal 474 disposed axially between the flange 441 and the radial side wall 432, directed towards the flywheel member 404, of the

annular form 430.

  Radially inside the side wall 432 and axially between the flange 441 and a radial zone 444 a, axially spaced from the latter, the flywheel member 404, there is provided a friction device 490 which is placed at the outside of the annular chamber 430 at least partially filled with viscous agent This friction device 490 operating dry comprises a friction disc 494 and on either side of the friction rings 494 a, 494b, the friction ring 494b being disposed

  axially between the friction disc 494 and the flange 441.

  On the side of the friction ring 494b which is opposed to the friction disc 494, there is provided an application disc 493, which is biased by an elastic disc 492, maintained

  axially between the radial zone 404a and the application disc

cation 493.

  The friction disk 494 has on its periphery

  outside of the 495 radial zones, which can

  to come into contact with counter-profile areas 494 a

  formed on the radially inner edge of the wall 432.

  The profiled zones may, depending on the intended application, be mounted without clearance or, however, present, in a circumferential direction, a certain angular clearance between the friction disk 494 and the wall 432, so that the friction device 490 can go into action only

  after the intervention of at least one of the

weaver 413.

  In the assembly 501 diagrammatically shown in FIG. 10, it is provided radially inside the damper 513 and on each side of the flange 541 and in

  an area adjacent to the annular channel housing 551

  a respective gasket 574, 574a, both

  seals cooperating in a sealed manner with corresponding zones

  adjacent portions 532, 531 which delimit the housing 551 in the form of an annular channel.

  The flange 541 is held radially in the

  inside the seals 574, 574 a, between two disks

  593, 594 with interposition of friction ring 594 a, 594 b.

  The disc 594 is rigidly connected to the flywheel member 504 via spacing pins 567. The application disc 593, axially disposed between the flange 541 and the radial zone 504a of the flywheel member 504, is biased by an elastic disc 592, which is held axially between this application disc 593 and the radial zone 504a Radially inside, the elastic disc 592 and the application disc 593 comprise recesses,

  which at least partially surround the space pins

  567 so that the elastic disk 592 and the application disk 593 can not rotate relative to each other.

to the steering wheel element 504.

  The prestressing force of the elastic disc 592 determines the moment under which the flange 541 can

  rotate or skate with respect to the flywheel member 504.

  Components 592 to 594b thus constitute, in connection with

  the radially inner zones of the flange 541, a coupler

  In order to limit the relative rotation between the flange 541 and the flywheel element 504, the flange may comprise in its inner zone projections which, considering the circumferential direction, engage radially between the flanges 541 and the flywheel element 504. spacer pins 567 By abutment of these radial protrusions

  of the flange 541 against the spacing pins 567, the rotation

  may be limited For many cases of

  However, it may also be advantageous if there are no such means limiting the relative rotation between the flange 541 and the flywheel member 504. In such cases, the coupling 590

  is designed so that the moment that can be trans-

  put by it is greater than the nominal torque at the

motor output.

  According to a variant of the device

  10, it is possible, in the case of a limited relative rotation between the flange 541 and the flywheel element 504, that additional energy accumulators, in the form of coil springs, enter

  in action between the two disks 593, 594 and the flange 541.

  These springs can be housed in corresponding recesses

  two discs 593, 594 and the flange 541, to which

  these recesses considered in a circumferential direction

  may be arranged between the space pins-

  567 With such an arrangement of the device, it is

  advantageous that the springs placed in the area of the

  by force conjugation (or the friction device 590 have a rate of elasticity substantially greater than that

  Springs of the outer damper 513.

  Also, the friction damping generated by the friction device 590 must be substantially greater than the friction damping occurring in the angular range of rotation of the damper 513 and which is, among other things, generated by the seals.

  574, 574 a which apply against the flange 541.

  In the embodiments described, it is also possible to obtain between the corresponding flywheel elements a multi-stage elasticity characteristic curve by the fact that at least some springs of a group of springs or a shock absorber are shorter than the angular spacing between the abutment or urging areas cooperating with them Also by using springs which are shorter than the annular channel sectors or the cutouts or windows receiving them, it is possible to obtain a angular range of rotation, free of return, between the two flywheel elements from a central position or a rest position This angular range can for example be established in the case of an embodiment such as that shown in Figures 5 and 6 by doing

  so that the springs 245 have, in a circumferential direction,

  fential, a smaller annular dimension than the angle

  between the branches 244 or the stops 255, 255 a.

  Of course, the present invention is not

  limited to the embodiments described and shown; it is capable of numerous variants accessible to those skilled in the art, depending on the applications envisaged and

  without departing from the spirit of the invention.

Claims (37)

  1 device for damping oscillations between a motor and a clutch in a transmission line, comprising two flywheel elements (3, 4) which are coupled by means of a damping system, flywheel members (3) can be connected to the output shaft of one motor and the other flywheel member (4) has a counter-friction surface for driving the friction disk ( 9) of the clutch, o one of the elements (3) steering wheel (2) comprises portions which form a chamber which defines by its radially outer regions a housing (51) of annular shape which is filled at least in part with a viscous agent and in which are received and supported in a circumferential direction energy accumulators (45) can be biased in both directions of rotation, o the portions delimiting the annular-shaped housing in one of the elements (3) of the steering wheel (2) axially cover the accumulators of energy (45) and support them against centrifugal forces, where the portions delimiting the annular housing (51) in one of the flywheel elements are supported by a disc-shaped component (31), which can be coupled, by via radially inner regions, with the output shaft of the motor, and further support areas of a disk-shaped flange (41) penetrate into the annular housing (51) so as to be able to solicit the energy accumulators (45) and transmit a torque to the other element of the steering wheel.   2 Device for damping oscillations between a motor and a clutch in a transmission line, comprising two flywheel elements (3, 4) which are coupled by means of a damping system, flywheel members (3) can be connected to the output shaft of one motor and the other flywheel member (4) has a counter-friction surface for driving the friction disk ( 9) of the clutch, o one of the elements (3) of the steering wheel (2) comprises portions which form a chamber which defines by its radially outer areas a housing (351) of annular shape which is filled at least in part with a viscous agent and in which are received and supported in a circumferential direction S energy accumulators (345) being able to be biased in both directions of rotation, o the portions delimiting the annular-shaped housing in one of the elements (3) of the steering wheel (2) axially cover the accumulators rs energy (345) and support against centrifugal forces, and further support areas of a disk-shaped flange (341) enter the annular housing (351) so as to solicit the accumulators energy supply (345) and transmit a torque to the other element of the steering wheel, and where the ends of the energy accumulators (345) are provided with intermediate pieces (359) through which the energy accumulators ( 345) can be biased and their ends retained, in opposition to the action of the centrifugal force, radially with respect to the outer wall, which is constituted by the annular portions of the housing (351) which axially cover the accumulators energy (345).   3 Apparatus for damping oscillations between a motor and a clutch in a transmission line, comprising two flywheel elements (3, 4) which are coupled by means of a damping system, flywheel members (3) can be connected to the output shaft of one motor and the other flywheel member (4) has a counter-friction surface for driving the friction disk ( 9) of the clutch, o one of the elements (3) steering wheel (2) comprises portions which form a chamber which defines by its radially outer regions a housing (51) of annular shape which is filled at least in part with a viscous agent and in which are received and supported in a circumferential direction energy accumulators (45) which can be biased in both directions of rotation, o the portions delimiting the annular housing (51) in one of the elements (3). ) of the flywheel (2) axially cover the accumulat energy carriers (45) and support them against centrifugal forces, and further support areas of a disk-shaped flange (41) penetrate the ring-shaped housing (51) so as to be able to solicit the accumulators energy supply (45) and transmit a torque to the other element (4) of the steering wheel (2), and o the energy accumulators (45) allow between the two elements (3, 4) of the steering wheel (2) to minus a relative rotation of + 25 degrees, from from a central position.   4 Apparatus for damping oscillations between a motor and a clutch in a transmission line, comprising two flywheel elements (3, 4) which are coupled by means of a damping system, flywheel members (3) can be connected to the output shaft of one motor and the other flywheel member (4) has a counter-friction surface for driving the friction disk ( 9) of the clutch, o one of the elements (3) steering wheel (2) comprises portions which form a chamber which defines by its radially outer regions a housing (51) of annular shape which is filled at least in part with a viscous agent and in which are received and supported in a circumferential direction energy accumulators (45) which can be biased in both directions of rotation, o the portions delimiting the annular housing (51) in one of the elements (3). ) of the flywheel (2) axially cover the accumulat energy carriers (45) and support them against centrifugal forces, and further support areas of a disk-shaped flange (41) penetrate the ring-shaped housing (51) so as to be able to solicit the accumulators of energy and pass on a couple to another steering wheel element.   Device according to one of Claims 2 to 4, characterized in that   the parts of one of the flywheel elements (3) defining the annular housing (51) are supported by a disc-shaped component (31) which can be coupled to the output shaft of the engine by   via radially inner zones.   6 oscillation damping device according to one of   Claims 1 to 5, characterized in that the chamber (30) is formed in   directly to radially oriented parts of the component (31) in the form of a disk.   7 Oscillation damping device according to one of the   Claims 1 to 6, characterized in that the shaped component (31)   disc carries a ring gear (40) starter.   8 Device according to one of claims 4 to 7, characterized in that   that the springs (45) can rest against radial branches (44) formed by the flange.   9 Oscillation damping device according to one of the   Claims 1 to 8, characterized in that the ends of   energy accumulators (45) can be solicited via of spacers (59).   Device according to claim 9, characterized in that the intermediate pieces (59) are adapted, at least in one zone   radially outer, the section of the housing (51) of annular shape.   11 Device according to one of claims 9 and 10, characterized in   that the ends of the energy accumulators (345) are retained by the intermediate parts (359) in opposition to the action of the centrifugal force, radially with respect to the outer wall which is constituted by the parts of the housing (351) annular shape that   axially cover the energy accumulators.   12 Device according to one of claims 1 to 11, characterized in that   the bearing zones (344) transmitting the torque to the second inertia mass (4) comprise profiled portions (344a) via   from which the intermediate pieces (359) are retained radially.   13 Device according to one of claims 9 to 12, characterized in that   that the intermediate pieces (359) penetrate through the profiled extensions in a circumferential direction in the extreme zones of the accumulators (345) of energy.   Apparatus according to claim 13, characterized in that the   extensions have a conical profile.   Device according to one of claims 1 and 2, and 4 to 14,   characterized in that the energy accumulators (45) allow between the two elements of the steering wheel at least a relative rotation of + 25 degrees, at from a central position.   Device according to one of Claims 1 to 15, characterized in that   that the elasticity rate resulting from the energy accumulators (45), provided in the annular housing (51), has in at least one relative rotational angle of 15 between the two elements (3, 4) of the flywheel ( 2) and from a central position, an order of magnitude between 2 and 20 Nm / degrees.   Device according to one of Claims 1 to 15, characterized in that   the energy accumulators (45) extend over 70 to 96% of the angular periphery of the device.   Device according to one of Claims 4 to 17, characterized in that   that the annular housing (51, 251) is created by two bodies (31, 32; 231, 232) in the form of shells.   19 Device according to claim 18, characterized in that at least one of the shell-shaped bodies (231, 232) is a profiled piece in jail.   Device according to Claim 18, characterized in that the annular-shaped housing consists of two parts (231, 232)   shaped sheet metal shaped half-shells.   21 Apparatus according to one of claims 4 to 20, characterized in that   that the supports for the springs (45) consist, in a circumferential direction, of elements (56, 57) arranged in the housing (51)   ring-shaped, which is otherwise continuous on its periphery.   Device according to one of the preceding claims,   characterized in that the supports for the springs (245) are formed in a circumferential direction by shaped portions in the form of pockets (255 c, 255 d).   Device according to one of Claims 4 to 22, characterized in that   at least one branch (144) of the flange has a smaller dimension -   considering a circumferential direction that the supports (155, a), provided on either side of this branch, in the housing of annular form.   24 Device according to claim 9, characterized in that the intermediate pieces (59) form, in the housing (51) form   annular, delivery pistons of the viscous agent.   Device according to one of the preceding claims, characterized   in that there is provided radially inside the annular housing (51) at least one other group of springs (48) forming part of the means of depreciation.   Device according to claim 25, characterized in that the flange (41) has radially outer recesses, which are separated from each other in a circumferential direction by radial branches (44) and in which the accumulators are received. of energy (45) of the first group, and is provided with windows (47) located radially further inwards, which are separated by radial tongues and in which the energy accumulators (48) are arranged. from the other group.   Apparatus according to one of claims 25 and 26, characterized in that   the first group of energy accumulators (45), or springs, provided in the annular housing (51), and the other group of energy accumulators (48), or springs, situated radially more inside, are arranged in parallel between the elements (3, 4) flywheel (2).   28. Device according to one of claims 25 to 27, characterized   that the groups of springs (45, 48) are arranged in a staggered manner, i.e. say with an angular offset.   Device according to one of Claims 25 to 28, characterized   at least some springs of at least one group (45, 48) of springs   are arranged staggered, that is to say with an angular offset.   Device according to one of Claims 25 and 26 or 28 and 29,   characterized in that the first group of springs, provided in the annular-shaped housing, and the other group of springs, located radially further inward, are arranged in series between the elements steering wheel.   31 Apparatus according to one of claims 18 to 30, characterized in   the housing halves or shell-like bodies have axial cells (63, 64) for receiving the inner group of springs (48).   Apparatus according to one of claims 4 to 31, characterized in that   that the inner springs (48) and / or the outer springs (45) bear radially, at least under the effect of centrifugal forces, against the catches (49) of the flange (41) hanging on them in one direction circumferentially.   33 Device according to one of the preceding claims,   characterized in that the springs of the inner group are housed in windows of two disks (593, 594), which are in rotational connection with the other flywheel element (504) which can be coupled with the transmission line, and receive axially between them a flange (541) ensuring the series coupling of the radially outer spring unit with   the group of radially inner springs.   34 Device according to one of claims 4 to 33, characterized in that   one of the flywheel members (204) comprises a component (227), having a certain profile, of an axially interlocking connection while   the other flywheel member (203) includes the counter component (241)   profile of the interlocking connection (242) providing the coupling connection   rotating two flywheel elements (203, 204).   Device according to Claim 34, characterized in that the groups of springs (45, 48) of the damping system are housed in a chamber (30) which can be filled at least partially with a viscous or pasty agent and which is constituted essentially by the components (31, 32) of a flywheel element (3) which can be coupled with the engine while the output portion of the damping system is constituted by a component (41) in flange shape which has   profile areas (72) that can be brought into contact with counter-zones   profile (73) provided on the other element (4) of the steering wheel (2), and furthermore one of the flywheel elements carries a sealing element (74) which, when the two elements (3, 4) ) steering wheel (2), comes to apply   sealingly against a surface (76) of the other flywheel element.   36 Apparatus according to any one of the claims   previous, characterized in that the flange-shaped outlet portion (41) of the damping system is mounted floating between the two casings (31, 32) or the shell-like bodies.   the flywheel element (3) can be coupled with the engine.   37 Apparatus according to any one of the claims   preceding, characterized in that the volume of the viscous agent received in the chamber (30) is dimensioned so that the second group   springs (48) at least partially penetrates this agent.   38 Apparatus according to one of the preceding claims,   characterized in that at least one friction device (90) acts between the steering wheel elements.   39 Device according to one of the preceding claims,   characterized in that between the flywheel elements acts at least one friction device (490), having a play in a circumferential direction.   40 Device according to one of the preceding claims,   characterized in that there is provided, outside the volume (430, 551) at least partially filled with viscous agent, as a pasty agent, additionally a friction damping device (490, 590)   dry acting between the two steering wheel elements.   41 Device according to one of the preceding claims,   characterized in that there is provided between the flywheel members (501) at least one friction damping device (590) which is placed in   series with the springs (513) acting between the aforesaid elements.   42 Apparatus according to one of the preceding claims,   characterized in that the friction damping and / or the viscous damping acting in parallel with the inner spring unit (48) is substantially smaller than the viscous damping and / or the friction damping acting in parallel with the group spring outer (45).   Device according to one of the preceding claims,   characterized in that at least some of the springs (45) are shorter   the arc portion between the stops (44, 55, 55 a).