FR2472693A1 - TWO-STAGE TORSIONAL VIBRATION DAMPER - Google Patents

Abstract

TORSIONAL SHOCK ABSORBER ASSEMBLY FOR REALIZING A LONGER TRAVEL FOR THE DAMPING EFFECT WHICH IS PROVIDED BY THE USE OF TWO CONCENTRIC SERIES OF DAMPER SPRINGS 73, 74, 75, 76, 77, 78 CONNECTED BY INTERMEDIATE WITH A COMMON ENCLOSURE OR AN INTERMEDIATE BODY. A DRIVE PLATE HAS AT LEAST TWO 28 FIXED DRIVE LEVERS ABOVE, THESE LEVERS EXTENDING INTERNALLY IN THE PATH OF THE OUTER CIRCLE OF THE DAMPING SPRINGS 73, 74, 75. AT LEAST ONE FLOATING DIVIDER RING 68 IS MOUNTED IN THE SET AND EARS 66, 69 SURFACE IN THE PATH OF SPRINGS LIKE THE OUTSIDE DRIVE BELTS 55 OF THE INTERMEDIATE BODY. MOUNTS OR MOBILE SKATES 81 ARE PROVIDED BETWEEN THE SPRINGS 76, 77, 78 OF THE INTERNAL CIRCLE WITH INTERNAL DRIVING BELTS 61 OF THE INTERMEDIATE BODY AND OF THE ARMS OF THE HUB 97 IN THE ROAD OF THE INTERNAL SPRINGS; THE HUB 93 BEING DRIVEN THROUGH SPRING CIRCLES TO DRIVE A TRANSMISSION INPUT SHAFT.

Description

1.

A torsional vibration damper is used

  used in a clutch for the drive train of a manual transmission of a motor vehicle in order to neutralize the torsional vibrations created by the vehicle engine which would otherwise cause characteristics

undesirable; for example, impact charges, pulses

  tions, noises, etc. in the transmission and the drive chain of the vehicle in operation. In addition, a

hydraulic torque converter or fluid coupling

  of for an automatic transmission having a clutch to

blocking to increase fuel economy through

direct training between entry and exit

  liquid coupling, at high speed, requires

vibration weaver. However, the vibration dampers

prior art were of limited utility to

  se of the relatively short arc of relative displacement between

the driving and driven parts of the shock absorber in the clutch

  ge. In order to overcome these drawbacks, a vibration damper with a longer stroke has been substituted for the usual short arc dampers. Such shock absorbers, described in patent applications No. 801,989 of May 31, 1977, No. 860,348 of December 14, 1977, and No. 45,711 of June 5, 1979 and the patent of the United States of America No. 4,139,995, 2. provide a larger stroke, especially in

  a lock-up clutch for torque converter. However

However, there have been cases where an even larger race

for a vibration damper was required, and the present invention provides for this longer stroke. 1

  The present invention relates to a damped assembly

  two-stage torsional vibration generator, which can be used in a lock-up clutch for converter

  torque and can have a relative displacement between the

  motors and leds of the shock absorber larger than those

previously obtained. The more the relative displacement arc in

  the driving and driving organs is large, the weaker is

  the depreciation rate. Under certain operating conditions

  the engine and transmission of the vehicle,

want a lower depreciation rate than the lowest

ble of the rates obtainable in the shock absorbers

above, and this low rate can be achieved with the

  present two-stage damping device.

  The present invention also relates to a torsional vibration damper assembly which, because of its very

low depreciation rate, increases hydraulic depreciation

  Specific to a hydraulic torque converter for

  vehicle. In the absence of a lock-up clutch, the

torque sor acts to hydraulically dampen vibrations

undesirable reactions, resonance, etc .; however, depreciation

  Separate valve is required with the addition of a lock-up clutch. The shock absorber of the present invention at stroke

larger provides a sufficiently low depreciation rate

ble to allow effective hydraulic damping of the torque converter and increased efficiency

vibration damper.

The present invention further relates to an improved two-stage torsional vibration damper assembly having two concentric circles of springs

  arranged in a housing and driven by support arms

drag mounted on a drive member, such as a 3. piston plate for the locking clutch. Floating members separate the springs in both the inner and outer circles of springs, and at least two groups of springs in each circle are operated in parallel, with the springs of each group acting in series. The present invention also provides an improved two-stage torsional vibration damper assembly having concentric circles of springs, the springs in the outer circle being driven by drive levers and separated inside the spring groups by floating dividing rings having dividing arms between the adjoining springs. In the inner circle of springs driven by band members in the retaining housing, shims or movable pads, which can move in the retaining housing, separate

contiguous springs. The inner spring groups drive

  the arms of a connected hub member last

  tional to the input shaft of the vehicle transmission

  cule. The present invention further provides a two-stage torsional vibration damper assembly having concentric circles of springs arranged in at least

two groups, o the springs inside each group

pe are separated by wedges or floating pads.

The present invention also provides a set

  two-stage torsional vibration damper that pro-

owes a low damping rate with a maximum arc of relative displacement between the driving and driven members of

  900. The device has an outer circle of springs available

in three groups operating in parallel with three sets of springs in each group, and an inner circle of springs arranged in two parallel groups of three

spring sets each.

The present invention will be clearly understood on reading

ture of the following description made in conjunction with

attached drawings in which: Figure 1 is an exploded rear elevation view of the two-stage vibration damper; Figure 2 is an enlarged sectional view of the shock absorber taken along line 2-2 of Figure 1 in a torque converter assembly; Figure 3 is an enlarged partial sectional view taken along line 3-3 of Figure 1 Figure 4 is an enlarged partial sectional view taken along line 4-4 of Figure 1; Figure 5 is a rear elevation view of the front retaining plate for the assembly; Figure 6 is a sectional view of the front retaining plate taken along line 6-6 of Figure 5; Figure 7 is a partial sectional view taken along line 7-7 of Figure 5; Figure 8 is a rear elevation view of the rear retaining plate; - Figure 9 is a sectional view of the rear retaining plate taken along line 9-9 of Figure 8; Figure 10 is a partial sectional view taken along line 10-10 of Figure 8; Figure 11 is a partially sectioned side view of the interior sliding divider in the working position; Figure 12 is an exploded perspective view of an interior sliding divider; Figure 13 is a rear elevation view of a second embodiment of a two-stage vibration damper;

Figure 14 is a partial sectional view of the

appears to be taken along line 14-14 of Figure 13; FIG. 15 is a side view partially in section of an external sliding divider in the working position;

Figure 16 is a side view of a split divider

smoothing outside;

  Figure 17 is a view along one of its ends.

  external sliding divider units; Figure 18 is a horizontal sectional view of the divider taken along line 18-18 of Figure 16; Figure 19 is a partial sectional view taken along line 19-19 of Figure 16; Figure 20 is a perspective view of a support plate for the divider;

Figure 21 is a rear view in partial elevation-

exploded view of a third embodiment of a cushioning

two-stage vibration weaver;

  Figure 22 is a sectional view of the cushioned assembly.

  weaver taken along line 22-22 of Figure 21; Figure 23 is a partial sectional view taken along line 23-23 of Figure 21; and Figure 24 is a partial sectional view taken on

  along line 24-24 in Figure 21.

With particular reference to the modes of exe

  cution shown in the drawings, Figures 1 and 2 shown

  feel a two-stage torsional vibration damper assembly 10 used in a lock-up clutch 11 for

  torque converter 12. The torque converter includes

takes an enclosure 13 driven by the output shaft of a

engine (not shown) having a front cover 14 with an over-

  annular clutch face 15 made on the inner surface

and a rear cover 16 operatively connected to a rotor (not shown). A turbine 17 is located in the

front part of the enclosure and is fixed at its periphery

  18 to a turbine hub 19 having internal splines 21 for receiving the splined end of a transmission input shaft 22. A stator (not shown) is

also positioned appropriately in the enclosure.

A piston plate 23, axially movable, comprising

  te an annular friction surface 24 close to the periphery

  external line cooperating with the surface 15, making the em-

  lockable clutch 11, and an inner annular flange 25 slidably mounted on a bearing 26 and sealed

by an annular sealing ring 27 mounted in a groove

  bearing age. The piston plate 23 and the damped assembly

seur 10 are both located in the space between the cover 6.

before 14 and the casing of the turbine 17.

  The vibration damper assembly 10 comprises three circumferentially spaced drive levers 28 fixed at their base 29 to the piston plate 23 by at least two rivets 31, the levers extending radially inward of an enclosure formed by a front retaining plate

  32 and a rear retaining plate 33. To allow the

  In order to move relative to the enclosure, the substantially parallel peripheral flanges 37, 52 of the plates 32, 33 are fixed together at a plurality of points along the circumference using pins 34; each pin having an enlarged central part 35 which acts as a spacer between the flanges with the ends 36 of the pins in

protrusion in the openings 38.53 of the flanges and inverted.

Thus, the flanges are spaced from each other by the par-

ties 35 to allow the levers to extend inward

laugh and move relative to the enclosure.

  The front retaining plate 32 is circular with an irregular sectional shape as shown in FIGS. 5,

  6 and 7, and comprises an annular peripheral flange 37 for-

  seen from openings 38 for rivets or pins 34, a

  part of the intermediate body 39 connected to the peripheral flange

risk by three external drive members 41, and an internal peripheral part 42 which is generally conical and is connected to the intermediate part 39 by a pair of link arms 43, arranged in opposition; each link arm having a central internal drive band 44

deported inward.

  The external drive members 41, in conjunction with

  tion with the peripheral flange 37 and the intermediate part

re 39, define three notches or openings 45 elongated

  arc-shaped for groups of external spring

  weaver 73, 74 and 75; each opening being further defined by an external arc-shaped lip 46 on the flange 37

and an arc-shaped inner lip 47 on the inner part

  intermediate 39. Similarly, the link arms 43 in conjunction

  tion with the intermediate part 39 and the internal part 7.

  42 define a pair of notches or openings 48 extending

arc shaped for interior spring groups

  damper 76, 77 and 78; the intermediate part 39,

  bearing a spring retaining lip 49 extending in the opposite direction to the lip 47. The inner periphery

  rieure 42 converges internally towards a central opening

the 51.

The rear retaining plate 33 includes a flas-

that peripheral 52 having circumferential openings 53

spaced apart to receive the pins 34 and a

  tie of the central body 54 connected to the peripheral flange by three drive members 55 also spaced around a circumference. The drive members define three

notches or openings 56 in the shape of an arc, generally

  axially generated with the notches 45 and having external lips 57 on the flange 52 and internal lips 58 on

the body part 54r The central body part 54 is bos-

backward to make closed housings 59 for shock springs 76, 77 and 78 and has a pair

  internal drive belts 61 arranged in an op-

  posed, deported inwards. The body part ends

  ve in a radial flange 62 extending inwards which

  defines a central opening 63 generally aligned axia-

Lement with the opening 51 of the front plate 32.

  A pair of dividing rings 65 and 68 is mounted on an annular flange 64, extending rearward, of the front retaining plate 32; the ring 65 having three separation arms 66, slightly offset backwards, also spaced apart on a circumference, extending radially towards

  outside and ending with fingers 67 extending cir-

  conferenceally. Likewise, the ring 68 has three separation arms 69, offset slightly backwards, also spaced apart on a circumference, extending radially outward to end with fingers 71 extending circumferentially. The arms 66 and 69 are offset opposite, so that they extend together with their respective fingers 67 and 71, in a guide channel 72 formed between 8. the peripheral flanges 37 and 52 and the outer lips

46 and 57 of the front and rear plates, respectively.

  Three groups of shock absorber springs 73, 74 and operating in parallel, with the springs of each group operating in series, are located between the external drive members 41 and 55 of the plates 32 and 33 and

  the arms 66 and 69 of the rings 65 and 68. Similarly, two groups

  weight of shock absorber springs 76, 77 and 78, operating in

parallel, are located in the cells 59 of internal springs

  between the drive belts 44 and 61 and pa-

  sliding dividers 79 and 81. Each divider includes

takes a part of a conical body 82 ending at its large end with a sliding part 83 in the shape of an arc, extending circumferentially from both sides

divergent 84, 84 from the body part. A tie of divi-

  sor 85 of a pair of sides 86, 86, diverging outwards

  laughing, connected by a rounded connecting part 87 adjusts

  both on the conical body portion 82 of each divider; the arms ending in flanges 88, extending outwards, coming into contact with interior surfaces of the arc-shaped parts 83. The sides 86, 86 extend outwards in 89 at- beyond the width of the conical body part in order to be in contact with the springs

damper 76, 77, 78. The sliding parts 83 of the di-

  sights come into contact with a guide surface 91 produced on the part of the central body 54 of the plate 33, and the extended sides 89 are mounted in the spring cells

59 between the plates.

A hub 92 includes a body 93 with grooves

  internal res 94 connected with external splines 95

  read on the turbine hub 19 and a plate or flange

  96 of hub assembled to the body and extending between the plates

ques 32 and 33 at their internal peripheries. The flange 96

takes a pair of diametrically opposite hub arms 97, 97 extending between the pairs of drive belts 44 and 61 and being generally axially aligned therewith; the arms having sides 98 diverging outwards and 9.

  ending in fingers 99 extending circumferentially-

  lie in the opposite way. Thus, the hub arms 97 are in

  the path of the interior shock springs 76, 77 and 78.

The radial flange 62 of the rear plate 33 is also

  tee on the body 93 of the hub. The arcuate outer lips 46 and 57 of

  plates 32 and 33 have reentrant ramps 101 and 102, res-

pectively formed near the drive members 41 and both act as retaining elements for

  springs 73 and 75 and as inclined planes to avoid

ter an outward movement of the springs when the drive levers 28 are spaced from the members 41, 55

  during a depreciation transaction.

  During the torque converter operation

  12, the oil flowing in the blades of the rotor, in the tur-

bine and in the stator also fills the enclosure 13 of the conver-

  torque weaver, and, when the oil pressure increases with the increase in the speed of rotation of the turbine 17, the oil pressure gradually stresses the plate of the piston 23 and the damper assembly 10 connected to the left

of Figure 2, to cause the contacting of the surface

  this friction of the piston plate with the surface 15 of the

  front cover 14 to block the rotor and the turbine of the

  couple weaver and produce a direct drive mode.

  Assuming that the piston plate rotates anti-clockwise (Figure 1), the piston plate 23 and the drive levers 28 begin to rotate when the clutch surfaces come into contact with each other.

the stationary damper enclosure.

  When the drive levers move in-

  be the flanges 37, 52 of the retaining plates 32, 33, they come into contact with the shock absorber springs 73 to compress the springs. The springs 73 stress the ring

  rear divider 68 via arms 69 for

priming the springs 74; these springs in turn urge the arms 66 of the front divider ring 65 to compress the

  springs 75. These springs act in their turn on the organ-

  10. external drive nes 41, 55 of the plates 32, 33 for

  rotate the plates relative to the hub 92. The rotation

tion of plates 32 and 33 causes campressiOn by the ban-

  inner drives 44, 61 of the pair of springs 76, and these springs come into contact with the sliding dividers 79 and move them to compress the springs 77; the springs 77 moving the sliding dividers 81 to compress the springs 7.8. The compression of the springs 78 urges the arms 97 of the hub 92 to rotate the body of the hub 93 and the turbine hub 19 to result in a rotation of the transmission input shaft 22. Thus, the assembly absorbs all the vibrations or any noise etc. in the drive train with an arrangement using three groups of external springs 73, 74, 75 in parallel

and two groups of inner springs 76, 77, 78 in parallel

the; the springs of each group acting in series.

  Figures 13 to 20 show a second embodiment of a two-stage vibration damper similar to that shown in Figures 1 to

12, the similar parts having the same numerical references

with an index a. This embodiment uses two

  xth series of sliding dividers 103 and 104 in place of the front and rear dividing rings 65 and 68 shown

in Figures 1 to 12. These dividers slide on the

  external lenses 46a and 57a of the front retaining plate 32a and the rear retaining plate 33a, respectively. Dividers 103 and 104 are identical and made of sheet

  of stamped metal with sides 105 diverging outwards

  laughing having edges 106 pleated internally and connected by a rounded internal end 107, the sides ending

  at their outer ends by flanges 108 extend

  circumferentially and having position tabs

  stamped up 109 which are received in

openings 111 of a generally rectangular friction plate

  gular 110 resting on the flanges 108. The plate of fric-

  tion 110 comes into contact with the lips extending towards

  the outside 46a and 57a of the retaining plates with the pat-

l11.

your 109 received in the guide channel 72a between the flas-

  ques 37a and 52a to guide the movement of the dividers.

In operation, under the effect of the rotation of the piston plate 23a, the drive levers 28a move relative to the retaining plates 32a and 33a to come into contact with springs 73a. The compression of these springs urges them against the sliding dividers 103 to compress springs 74a, which in turn urge the sliding dividers 104 between springs 75a. The compression of the springs 75a causes the rotation of the retaining plates 32a, 33a under the action of the drive members

  41a, 55a, which results in a rotation of the driving bands

  44a, 61a, against inner springs 76a. The com-

pressure of the springs 76a urges the dividers 79a to compress the springs 77a which in turn urge the dividers 81a to compress the springs 78a, these springs

  coming into contact with arms of the hub 97a to rotate

ner hub 92a and cause the input shaft to rotate

of transmission.

Figures 21 to 24 show a third mode

of a 112-stage two-stage shock absorber assembly

  read to that of FIGS. 1 to 12, the similar parts having the same reference numbers with an incide b. The piston plate 23b is substantially the same as the plate shown in FIG. 2 except for an inclined part 113 on which a pair of drive levers 114, arranged in opposite directions, is fixed by screws 115 or similar fastening means. Each drive lever has a conical body part with surfaces 116 contacting the springs diverging towards the outside, ending in an arc-shaped base part 117, the lever having an inclined surface 118 resting on the piston plate, a substantially vertical opposite surface 119 and an upwardly extending guide flange 120. A circumferentially extending notch 121 also extends through

the tapered body part and in the base part.

A dividing ring 122 (FIGS. 22, 23 and 24) having 12. an inclined surface 123 resting on the piston plate 23b, is mounted on the drive levers, a flat 124 located below with an annular groove 125 receiving the guide flanges 120 and an integral inner flange 126 parallel to the generally vertical surface 117 of the levers. In opposite positions, the ring has a pair of thicker parts 127 extending inwards, each part ending in a conical divider 128 having surfaces coming into contact with the converging springs 129

  towards the inside. A pair of sliding dividers 130 (fi-

gures 21 and 24) are mounted to slide in the duct formed by the ring 122; each divider comprising a part 131 of conical body with surfaces 132 coming into contact with the springs converging towards the outside and a part

  133 arc-shaped base having an inclined surface 134 ve-

nant in contact with the inclined portion 113 of the piston plate, an arc-shaped surface 135 mounted below

  124 of the ring 122 and a flat surface 136 coming into contact

  sliding contact with the inner surface of the solid flange

re 126.

  An intermediate member 137 comprises a ring ex-

138 having a pair of arms 139 arranged in an op-

installed (figure 22> with sides coming into contact with the externally diverging springs, ending with

  fingers 141 extending circumferentially, and a ring

  142 connected to the outer ring by a pair of ban-

  drive units 143 arranged opposite and having

  sides 144, coming into contact with the springs, various

  giant outward; the bands being connected to the ring

  interior by offset parts 145.

An inner drive ring or hub 146 (Figure 22) includes an annular ring with a pair of

  drive legs 147 extending inwardly available

  opposite to surfaces coming into contact

with the springs converging inwards, and a flas-

  that 148 of annular hub, extending inward, if-

  killed in the back and being appropriately attached, e.g.

13.

  ple using bolts 149, to the turbine hub 19b of the

  couple vertisseur. The ring 146 and the legs 147 have

  elongated notches 151 extending circumferentially

receiving the drive belts 143 for relative rotation

  tive between the intermediate member 137 and the drive ring

ment 146. Two pairs of dividers 152, 153, having sur-

  faces coming into contact with the springs, converging inwards, are slidably mounted on

* the ring 146 to separate the internal shock absorber springs

  laughs 76b, 77b and 78b. The dividers 128 of the ring 122 and

  the sliding dividers 130 separate the shock absorber springs

exterior weaving 73b, 74b and 75b.

As shown in FIG. 16, two groups of shock absorber springs 73b, 74b, 75b act in parallel and two groups of interior shock absorber springs 76b, 77b, 78b act in parallel. Considering the operation of this assembly, a rotation of the piston plate 23b causes the displacement of the drive levers 114, compressing the springs 73b, which act on the dividers 128 of the ring 122 to compress the springs 74b, which at their turn act on the sliding dividers 130 to compress the springs 75b; the springs 75b acting on the arms 139 to cause the rotation of the intermediate member 137 by

  relative to the ring or to the drive hub 146. A displacement

cementing of the arms causes the rotation of the drive bands

  ment 143 to compress the springs 76b, which causes a sliding movement of the dividers 152 to compress the springs 77b, which results in a displacement of the dividers 153 to compress the springs 78b, and in turn causes

a rotation of the legs 147 of the ring-or drive hub-

  inner 146 to rotate the turbine hub l9b. Thus, a depreciation action up to a maximum of 900 is ensured

  by the damping devices of the present invention. The present invention is not limited to the examples

  which have just been described, it is

milking subject to variations and modifications which appear

will be understood by those skilled in the art.

14.

Claims (8)

  1 - Two-stage torsional vibration damper assembly (10) for the transmission of a torque between driving and driven elements, comprising a piston plate (23) functionally associated with coupling input means   ple, at least two drive levers (28) fixed to the plate as a piston, a hub (92) operatively connected to an ar-   output bre (22), characterized in that at least two means external floats (65, 68 or 103, 104) designed to move   cer according to an arc-shaped path around the hub, at least   two internal floating means (79, 81) intended to move   cer on a second arc-shaped path around the hub, concentric with the first arc-shaped path, a plurality of external damper springs (73, 74, 75) movable in the first arc-shaped path, a plurality of internal damper springs (76, 77, 78) movable in the second arc-shaped path, the drive levers (28) having protrusions extending inward of the first d-shaped path 'arc, and a rotary intermediate member (32, 33)   having at least two drive members (41, 55) extend   in the first arcuate path and at least two drive belts (41, 55) extending in the second arcuate path, the hub having at least two arms (97,   97) extending in the second arc-shaped path, the res-   external shock absorbers being interposed between the mo-   external floating yen and the drive members, and the internal shock springs interposed between the   drive bands and the second floating means.   2 - torsional vibration damper assembly according to claim 1, characterized in that the drive levers (28) are axially aligned with the drive members (41, 55) and the hub arms (97, 97) are axially aligned with the drive belts (44, 61)   in the absence of torque applied by the input means.   3 - Torsional vibration damper assembly   according to claim 2, characterized in that the flow means   both external comprises a pair of dividing rings (65, 68) 15. mounted on the intermediate member (32, 33) close to each other, each dividing ring having at least two arms extending towards the outer (66 or 69) separating the external damper springs, the dividing ring arms (66, 67) being partially offset internally towards the near ring to be positioned in a common plane, and in that the internal floating means includes two pairs of dividers   slides (79, 81) separating the shock absorber springs   dull, sliding dividers-on the intermediate organ- re (32, 33). 4 - Torsional vibration damper assembly,   according to claim 2, characterized in that the member in- intermediate includes a pair of retaining plates me irregular (32,33) connected together, being distant from each other, the drive members (41, 55) and the drive belts (44, 61) being integral with the plates   and that the retaining plates (32, 33) have   peripheral radial flanges (37, 52) distant from one another   be to receive between them the drive levers. (28) projecting in the external arc-shaped path of the   external shock absorber springs, at least one return plate held being mounted on the hub. - Torsional vibration damper assembly according to claim 4, characterized in that the plates   retainers have separate arc-shaped notches (45, 56)   rees by the drive members (41d 55) to receive   the external shock absorber springs and cells for   internal arc-shaped spells (59) receiving the internal shock springs, the drive bands (44, 61) being offset inwardly into the cells to extend in the path of the shock springs- internal,   and in that the arms of the hub (97, 97) extend radially-   outward from a hub body (93) in   the second arc-shaped path between the drive bands   internally deported (44, 61).   6 - Torsional vibration damper assembly   according to claim 2, characterized in that the flow means   16. both external has at least two pairs of dividers sliding (103, 104) which can slide on the inter-   middle (32, 33) and separating the shock absorber springs   external (73, 74, 75), and in that the floating means inter-   does not include two pieces of sliding dividers (79, 81) se-   covering the internal shock springs, and the   intermediate comprising a pair of retaining plates irregular shape (32, 33) with peri-radial flanges   spheres (37, 52) interconnected in a spaced manner, the drive members (41, 55) and the drive bands (44, 61) being integral with at least one retaining plate (33) being mounted on the hub.   7 - torsional vibration damper assembly according to claim 2, characterized in that it comprises a pair of oppositely disposed drive levers (114) having circumferential notches (121), the hub (146) having a flange annular (148) fixed to the outlet means (19b) and ending at its outer periphery by a ring (146), a pair of hub arms arranged so opposite (147) extending radially inwardly from   ring shot, and the intermediate member (137) includes a central ring (138) concentric with the hub ring   and an internal ring (142) connected to the central ring (143) - by the drive belts, the drive members   (139) extending outward from the central ring   tral in the notches (121) of the drive levers (114).   8 - torsional vibration damper assembly according to claim 7, characterized in that the ring (146) and the arms (147) of the hub have, located in opposite directions,   elongated notches (151) receiving the drive bands   ment (143), and in that the drive levers (114) include circumferential guide flanges (120) trained on it.   9 - Torsional vibration damper assembly   according to claim 8, characterized in that the floating means   both external comprises a divider ring (122) having a flange   as integral (126) and an annular guide notch (125) 17.   receiving the guide flanges (120), and a pair of dividers   spring sockets extending inwards, arranged in   opposite lesson, integral with the dividing ring and projecting inside the external arc-shaped path, a pair of sliding dividers (130) arranged in opposite manner, movable on a guide surface (124) of the ring, and further comprising two pairs of sliding dividers (152,   153) movable on the inner surface of the hub ring.