KR20000075510A - Torsional damper, in particular for lockup clutching of a hydrokinetic coupling apparatus - Google Patents

Abstract

The present invention relates to a torsional damper (3), which comprises an arm disk (6), a transition collar (8) with projections, two guide washers (4, 5), and an elastic member mounted in series (70, 71), an additional elastic member (7) is interposed radially between the transition collar (8) and the guide washers (4, 5) past the projection. The present invention is applicable to the lockup clutch.

Description

Torsional damper of hydrodynamic coupling device {TORSIONAL DAMPER, IN PARTICULAR FOR LOCKUP CLUTCHING OF A HYDROKINETIC COUPLING APPARATUS}

Such dampers are disclosed in French Patent Publication No. 2 393 199 and provide satisfaction because it makes it possible to increase the relative angular motion between two coaxial parts.

Nevertheless, the problem is raised for the satisfactory reduction of vibrations which are likely to occur along the entire dynamic chain into which the torsional damper is inserted, on the one hand the intermediate torque through the first large angular motion between the two coaxial parts It may be desirable to provide a transmission of, and on the other hand to provide a transmission of high torque at the end of the final angular motion between the two parts.

Summary of the Invention

It is an object of the present invention to meet these requirements simply and economically.

According to the invention, a torsional damper of the type described above has one of its axial parts having a damper plate with a radial arm while the other of the axial part has a side arm of the damper plate and each side of the diversion ring. With two guide washers disposed thereon, a coupling means having a play between the arm of the damper plate and the diversion ring is provided, and a third group of circumferentially acting elastic members is diverted with the guide washers. Acting between the rings, and wherein the third group of elastic members is disposed radially over the first and second groups of elastic members on the one hand and radially over the engagement means with the play on the other hand. It features.

According to the invention, the elastic members in the first and second groups of elastic members act in series in the first step until the play of the play means with the play is lost. Then, in the second step, the elastic members of the second group and the third group act in parallel.

As is known, their hardness is added when the elastic members act in parallel. When the elastic members work in series, it is necessary to add the reciprocal of the hardness in order to have the reciprocal of the hardness of the same spring.

Thus, it is possible to deliver medium torque in large motions in the first stage and high torque in the second stage in order to appropriately reduce vibrations. This will allow the simplicity of the torsional damper compared to that disclosed in French Patent Publication No. 0 744 563 using two rows of rivets.

In one embodiment, the hardness of the elastic members in the third group of elastic members is greater than the hardness of the elastic members in the first and second groups. As a variant, all the elastic members have the same hardness.

The present invention is simple because it results in the formation of a facing housing in the guide washer and the diverter washer for the attachment of the additional elastic member. In addition, the arm is elastically coupled with the switching ring because the switching ring is elastically connected to the damper plate and the guide washer.

In one embodiment, after the relative angular movement between the damper plate and the switching ring and the reduction of the play of the engagement means with the play thereafter, the arm engages a transverse shoulder that forms a stop and the stop is provided with a projection. Belongs to the directional protrusion. Therefore, the addition of material at this point strengthens the transition ring.

In one embodiment, the arms have studs extending circumferentially from the protrusions on their outer circumference. The studs cooperate with the shoulder after narrowing each play, and this stud belongs to the play means with the play.

The stud also supports the elastic members in the first and second groups.

As a variant, the arm has a 90 ° fold on its side to engage the shoulder after narrowing the side play.

In one embodiment, the third resilient member is mounted in a hole or the other housing is formed opposite the lug and the tongue, the diverting ring and the guide washer each having radial projections at their periphery, and according to one feature One of the tongues belongs to at least the axial dish-shaped region, thereby forming a shoulder at each distal end of the dish-shaped region, thereby restricting the relative angular movement between the guide washer and the transition ring by engaging the lug with the stop. To form a stop.

Thus, the guide washer and damper plate and the shift ring are not mechanically weakened by the rectangular or other openings.

In addition, the number of parts is reduced to facilitate the reduction of the radial volume.

In one embodiment, the guide washers are provided with contact tabs on their radial projections at their outer periphery. These tabs intersect with the tongue and lug to form tenons meshing with no mortars formed in the drive piston of any other torque transmission element, for example driven or driven.

Thus, a good transmission of torque is achieved while minimizing the radial volume of the friction damper.

Preferably, the tab of one of the guide washers has a fold on its side of approximately 90 ° to accommodate the tab of the other guide washer forming the reinforcing tab. This tab is touch type.

Thus, the tenon is high in strength and allows good sliding of the drive element relative to the guide washer because the flexible shaped fold interacts with the edge of the groove and is soft on its own. Due to the fold, the problem caused by the presence of burrs in the prior art is eliminated, and the torque transmission part and the guide washer are metal pieces achieved by cutting and folding. Such folds may have some torsional damper.

In addition, good contact area is achieved. This prevents the scaling phenomenon. Preferably, the fold has a height greater than the thickness of the guide washer in order to increase the contact area between the tab and the groove, to further reduce the scaling phenomenon and to further promote the slide.

There is a circumferential play between the fold and the tab on the other guide washer.

Thus, it is possible to fix the tabs on the two washers together by some means (riveting, welding, etc.) and to deform the fold so that the entire tab transmits torque.

Of course, the two guide washers can be fixed together at different points.

Of course, such a structure may be changed in such a way that the guide washer is fixed to the drive element, and in the above-described embodiment, the fixed damper plate may be shaped to be movable in the axial direction.

It will be appreciated that the fold may be elastically deformed due to tabs on other guide washers but not plastically deformed. In this way, the play of manufacturing tolerances is reduced, whereby the lugs are engaged without play by their folds in the associated grooves forming the dome holes in the drive element.

The following description sets forth the invention in conjunction with the accompanying drawings.

The invention relates in particular to a torsional damper for a lock-up clutch of a hydrodynamic coupling device. This torsional damper has two coaxial components mounted angularly with respect to each other as opposed to the first and second groups of elastic members mounted in series by a shifting ring, wherein the shifting ring comprises Radial protuberances interposed between the first elastic member in the first group of elastic members and the second elastic member in the second group of elastic members.

1 is a schematic axial sectional view of a hydrodynamic coupling device having a lockup clutch fitted with a torsional damper according to the present invention;

FIG. 2 shows the direction of arrow 2 of FIG. 1 with the torsional damper cut locally; FIG.

3 is a schematic view of the lockup clutch of FIG. 1, showing two positions of the piston;

4 is a partial view shown in the direction of the arrow 4 of FIG.

5 is a view in the direction of the arrow 5 of FIG.

6 is a graph showing characteristic curves of torsional dampers,

7 shows a deformed shape of a tab.

In the figure a torsional damper 3 for a lock-up clutch 1 of a hydrodynamic coupling device is shown.

The lockup clutch 1 is intended to be mounted inside an oil-filled sealing casing 100 of the hydrodynamic coupling device, which coupling device includes at least one impeller wheel 101 and a turbine having blades inside the casing. A wheel 102.

Typically, a reaction wheel 103 is provided to form a torque converter. The hydrodynamic coupling device is a startup torque transmission device, and as shown in the drawings, a drive shaft (not shown) (automotive engine when applied to an automobile) and a driven shaft (not shown) (gear when applied to an automobile) Between the input shaft of the motor box such as a box).

The casing 100 of the coupling device constitutes the input of the device, while the turbine wheel 102 constitutes the output of the device by the hub 106.

The casing 100 has two parts 104 and 105 fixed to each other, one of which is equipped with a blade of the impeller wheel and the other part 105 is referred to as a driving part, It is mainly shaped to be connected to the drive shaft by a diaphragm.

The hub 106 of the turbine wheel has a longitudinal groove formed therein to be rotatably coupled with the driven shaft.

Thus, the casing 100 is rotated by the drive shaft and rotates the driven shaft via the turbine wheel 102 which is rotationally driven by the circulation of oil between the impeller wheel 101 and the blade of the turbine wheel 102. Drive it.

After departure of the vehicle, slip occurs between the turbine wheel and the impeller wheel, since a lockup clutch 1 of known type is provided for directly coupling the casing to the turbine wheel.

The lockup clutch has a piston 2 defining a control chamber 108 with a horizontal wall 107. This transverse wall 107 is formed integrally with the drive part 105 of the casing intended to be fixed to the drive shaft. Thus, the annular metal piston 2 is disposed axially between the turbine wheel and the horizontal wall. The piston 2 is in a lateral orientation and is movably mounted axially relative to the transverse wall to fix at least one friction lining 21 between itself and the transverse wall. The friction lining is fixed to one of the piston 2 and the transverse wall 107 and acts outside of the piston 2 and defines the main pressure chamber 109 on the same side as its surface curved towards the turbine wheel. .

For example, by varying the pressure in the control chamber 108, the piston moves in the direction of the horizontal wall 107 or away from the horizontal wall.

This piston 2 is coupled to the hub of the turbine wheel by a torsional damper 3.

Thus, when the piston 2 moves axially in the direction of the transverse wall 107, the friction lining 21 is fixed between the transverse wall forming the reverse piston and the piston 2, thereby engaging the clutch and torque The converter is bridged. Thereafter, the motion is transmitted from the drive shaft to the driven shaft via the torsion damper 3, thereby reducing the vibration transmitted from the vehicle engine crankshaft to the input shaft of the electric motor box.

When the piston 2 moves in the opposite direction to the transverse wall by the pressure reversal in the control chamber, the friction lining is released and the lockup clutch 1 is disconnected or the bridge connection is released.

This is why the lockup clutch 1 is sometimes referred to as a bridging clutch.

All of these are known to those skilled in the art.

Likewise, in a known manner, the torsional damper 3 has two coaxial parts 4, 5 mounted rotatably mounted relative to one another, opposite the circumferentially acting elastic members 7, 70, 77, said The elastic member has at least one switching ring 8 for mounting at least some of them in series.

One of the coaxial components constitutes the input elements 4, 5 of the torsional damper 3 belonging to the lockup clutch 1, while the other of the coaxial components constitutes the output element 6 of the damper 3.

The output element 6 consists of a metal damper plate and has a transverse arm 60 projecting from the outside thereof, the transverse arm opposite to the axis of symmetry X-X 'of the hydrodynamic coupling device. To the outside in the radial direction.

The damper plate 6 has at its inner circumference a fixed portion 61 axially offset relative to the arm in the opposite direction of the piston 2, ie in the direction of the turbine wheel. This transversely facing fastening portion 61 provides a hole 62 for securing the damper plate 6 here to the hub 106 of the turbine wheel 102 by rivets (not shown for clarity). Equipped.

In addition, the switching ring 8 is made of metal and has a projection 80 projecting radially outwardly, that is, toward the axis X-X '. The number of these protrusions is equal to the number of arms 60 on the damper plate 6 and depends on the application example. The arm 60 and the protrusion 80 face in opposite directions in the radial direction.

The arm 60 intersects circumferentially with the triangular shaped projection 80 to support a portion of the resilient members 70, 71 consisting of coil springs.

Here, the three projections 80 in the lateral direction intersect in the circumferential direction with three arms 60 each having a circumferential stud 63 in the lateral direction on the outer circumference.

Thus, each arm 60 is provided with two studs 63 belonging to the engaging means with play 9 and is suitable for cooperating with the shoulder 83 described below.

The stud 63 forms a reverse stop.

The input section has two metal guide washers 4, 5.

The arm 60 of the damper plate 6 enters between two guide washers 4, 5 arranged on each side of the arm 60, with the diversion ring 8 surrounding the damper plate 6.

According to one feature, the guide washers 4, 5 have, on their outer periphery, columnar tongues 40, 50 having a greater circumferential length than the radial height.

These tongues 40, 50 intersect the lugs 41, 51 circumferentially, with each washer 4, 5 having a radial projection at its outer periphery. Lugs 41 and 51 and tongues 40 and 50 on one of the guide washers 4 and 5 are opposed to lugs 51 and 41 and tongues 50 and 40 on the other of the guide washers 4 and 5. do.

The number of tabs 41, 51 and tongues 40, 50 depends on the application.

Here, three tongues 40, 50 are provided for each guide washer 4, 5 and three tabs 41, 51 are on the guide washer between the two consecutive tongues 40, 50. 41, 51 and the distribution of tongues 40, 50 are regular.

Of course, tabs 41 and 51 and tongues 40 and 50 are higher in radial direction than in circumferential width. Tabs 41 and 51 are narrower in circumferential direction than tongues 40 and 50.

The diversion ring 8 has a transverse lug 81 at its outer periphery. These lugs 81 are arranged between two tongues 40, 50 opposite the respective guide lugs 4, 5, respectively. Thus, three lugs 81 are provided. These lugs 81 are longer in circumferential length than radial height, while they are shorter in circumferential direction than tongues 40 and 50 protruding on each side of lug 81 at the idle position of the torsional damper.

Lug 81 is positioned radially over triangular projection 80.

More precisely, the radial symmetry axis of the projection 80 is the same as the radial symmetry axis of the lug 81. Thus, the diverting ring 8 has a lug 81 and a projection 80 facing in the opposite direction of the radial direction, the projection 80 being shorter in the circumferential direction than the lug 81 and having a wedge shaped projection 80. The end of) is facing axis (X-X ').

The lug 81 is connected to the projection 80 by an annular portion 82 inclined toward the turbine wheel. Thus, the lug 81 is axially offset relative to the projection 80 in the opposite direction of the piston 2.

The outer circumferential portion (lug 81) of the switching ring 8 is axially offset with respect to the inner circumferential portion (protrusion 80) of the ring 8.

Similarly, the outer peripheral portion (arm 60) of the damper plate 6 is axially offset with respect to the inner peripheral portion (part 61) of the damper plate 6. The axial sleeve 64 connects the fixing portion 61 to the arm 60. These arms 60 are axially offset in the direction of the piston. As can be seen in FIG. 1, the fixing portion 61 is axially offset with respect to the outer peripheral portions of the guide washers 4, 5. Thus, the fixing portion 61 is axially farther from the arm 60 than the outer circumference of the guide washers 4, 5 is axially offset with respect to the inner circumference of the washer. Each guide washer has an inclined portion 42 which connects its inner circumference with an outer circumference consisting of tabs 41 and 51 and tongues 40 and 50.

The piston 2 and the transverse wall 107 with respect to the turbine wheel 102 in order to be able to receive the central portion of the torsional damper 3, ie the arm 60 and the inner circumference of the guide washers 4, 5. It will be appreciated that the center is concave in the shape of a dish in the axial direction in the opposite direction.

The inner circumference of the washers 4, 5 has three inner holes 53 of curved shape regularly distributed in the circumferential direction.

The guide washer 4 closest to the turbine wheel 102 has an axial flange 55 which surrounds the sleeve 64 of the damper plate 6 at its inner circumference. Each tongue 40, 50 has an outer hole 54.

Each lug 81 is opposite the hole 54 and has an outer hole 84 opposite from one guide washer to the other guide washer.

As can be appreciated and apparent from the figures, the inclined portion and the annular portion match the torsional damper to the shape of the turbine wheel and occupy the available space in the best possible range.

The outer holes 84 and 54 allow mounting of the elastic member 7, while the inner holes 54 allow mounting of other elastic members 70 and 71 according to one aspect of the invention. Here, the elastic members 7, 70, 71 are coil springs, and according to another feature, the tabs 41, 51 are rotatable to the piston 2 to move the guide washers 4, 5 in the axial direction. Allow to connect.

More precisely, the elastic members 7, 71 are arranged on the circumference of two stages of elastic members, i.e., 3 on the circumference of a diameter larger than the diameter of the second and first elastic members mounted in series. Two elastic members 7. The number of the third, second and first elastic members 7, 70, 71 is three and the third elastic member 7 is at the end of the moving coil spring. This third resilient member is concentric and has a greater hardness than the other resilient members 70, 71, each consisting of two concentric coil springs.

In addition, the third elastic member 7 is arranged radially over the coupling means with the play 9, in other words radially over the stud 63 and the shoulder 83.

The second elastic member 71 belongs to three elastic members 71 of the second group, while the first elastic member 70 belongs to three elastic members of the first group. The third elastic member 7 belongs to three elastic members 7 of the third group.

The elastic members 71 and 70 of the second and first groups are distributed along the same circumference and have the same hardness.

Of course, as a variant, the elastic members in the first group of elastic members may have a lower hardness than the elastic members in the second group, and the elastic members in the second group may be lower than the elastic members in the elastic group in the third group. It may have a hardness.

This depends on the application, and the damper 3 may or may not be actuated symmetrically.

Each projection 80 on the switching spring 8 has a second elastic member 71 and a first group 70 in the second group for mounting the second elastic member 70 and the first elastic member 71 in series. It is interposed between the 1st elastic members in ().

It is for this reason that the projection 80 has a triangular shape and has an arcuate (curve) shape for mounting two continuous members 70, 71 in the same hole 53 of large circumferential size.

In addition, the stud 63 on the arm 60 makes it possible to support the outer spring of the elastic members 70, 71 located on each side of the arm 60 in the radial direction outward.

According to another feature of the invention, the studs 63 have different functions because they are adapted to engage with the shoulders 83 belonging to the inner circumference of the switching ring, respectively. Thus, arm 60 is mounted to a circular scallop 86, respectively, and the switching ring 8 has its inner circumference between two successive shoulders 83. Thus, the diverting ring 8 has additional material at its inner circumference at the same height as the projection 80. Accordingly, three radial protrusions 85 are formed in the inner circumference of the diversion ring, and the three radial protrusions 85 are laterally defined by the shoulder 83 and the protrusions 80 in the center, respectively. In addition, the switching ring 8 is reinforced in the region supported by the three groups of elastic members. Thus, the scallop 86 is present in the inner circumference of the washer 8 between two successive protrusions 85.

As is known, each elastic member 70, 71 is composed of two concentric coil springs (outer springs surround the inner springs). A lot of torque is transmitted accordingly.

As a variant, each member 70, 71 is composed of a single coil spring or two or more multiple coil springs.

The outer circumference of the arm 60 is in intimate contact with the inner circumference of the switching ring 8 at its scallop 86. The switching ring 8 is thus centered by the damper plate 6, which applies equally to the guide washers 4, 5 which are centered by the flange 55 with respect to the sleeve having a dual function. do.

Therefore, the damper plate 6 functions as a center setting device of the guide washers 4 and 5 and the damper plate 6.

The spring 7 in the elastic group of the second group is floated and mounted in the holes 84 and 54 as disclosed in French Patent No. 97 07479 of 17 June 1997.

The length of these holes 84 and 54 is longer than the length of the stationary spring 7.

Thus, in the case of a stationary movement determined by the engagement means with the clearance 9 necessary for the acting acting of the spring 7, the length of the hole is reduced. For more detailed information, reference should be made to the aforementioned patent.

Each inner radial protrusion 85 is circumferentially longer than the lug 81 and the tabs 41 and 51.

With all these contrasts, lug 81 can be reduced in circumferential size and the diversion ring is reinforced by an inner radial protrusion 85 arranged in alignment with lug 81.

The guide washers 4, 5, the diverter ring 8 and the damper plate 6 are made of sheet metal and are obtained by cutting and / or bending on a press.

Accordingly, the outer hole 54 and the inner hole 53 in the guide washers 4, 5 may be defined by the curved edge 56 to match the cylindrical outer contour of the coil spring it receives.

Thus, the holes 53, 54 have a solid continuous contour which can adequately support the spring, in particular the spring 7.

The transverse shoulder 83 and the stud 63 constitute the above-mentioned engagement means having a play 9.

During the relative angular movement between the guide washers 4, 5 and the damper plate 6, the springs 70, 71 are operated in series until there is no circumferential play between the stud 63 and the shoulder 83.

Accordingly, the shoulder forms the first stop of the stud 83.

Of course, the shoulder 83 may be replaced with a different shape of the first stop.

More precisely, considering the relative motion of the fixed guide washers 4, 5 in the direction of the arrow F in FIG. 2, the arm 60 moves relative to the washers 4, 5 in a first step, It can be seen that the springs 70, 71 are compression mounted in series with the projection 80 by means of a switching ring 8, and the element 71 is supported on the associated lateral edge of the hole 53.

After narrowing the circumferential play between the stud 63 and the shoulder 83, the damper plate 6 drives the switching ring 8 directly by contacting the stud with the shoulder 83. Then, the second operating step is started.

During the second step, the second elastic member 71 and the third elastic member 7 are in parallel between the guide ring and the guide washer 4 and 5 fixed in relation to the rotation of the damper plate 6. It is possible to operate.

In the first step, the elastic members 70, 71 are operated in series and have a relatively low hardness.

In this second step, the elastic members 7, 71 are parallel and have high hardness. Thus, as shown in FIG. 6, the characteristic curve A—transfer torque C as a function of the relative angular motion D (X axis) between the guide washers 4, 5 and the damper plate 6 ( Y axis)-makes it possible to appropriately damp the vibrations.

In FIG. 6, it is an automobile engine which drives an automobile wheel (towing direction). When the wheel drives the engine (in reverse), the opposite occurs, and the first and second springs 70, 71 are operable in parallel in the second stage.

Of course, the angular movement between the diverting ring 8 and the guide washers 4, 5 is limited by the lateral edges 87 of the lug 81 which engage with the second stop 11 belonging to the guide washer. .

The second stop 10 is arranged radially over the coupling means having the first stop 83 and the play 9.

The formation of the first stop 83 and the second stop 10 is carried out without any additional member and without weakening the mechanical strength of the parts 4, 5.

More precisely, the tongue 50 on the guide washer 5 closest to the piston 2 is recessed axially in the axial direction in the opposite direction of the other guide washer, ie in the direction of the piston 6.

More precisely, the tongue 50 is not only concave in dish shape, but the annular region 58 is located on each side of each tongue 50 and extends close to the tab 51. In this way, the shoulder 10 is formed to form the stop 10 described above at the same height as connecting the region 53 to the tab 51.

The height measured in the axial direction of this shoulder 10 is a function of the thickness of the switching ring 8. Preferably, the axial height of the shoulder 10 is at least equal to the thickness of the diversion ring. The axial height of the shoulder 10 is greater than the thickness of the diverting ring 8, so that there is a very small axial play between the diverting ring 8 and the guide washers 4, 5.

During the second step, the diverting ring 8 and the guide washers 4, 5 until the lateral edge 87 of the lug 81 engages the stop 10 in the region 58 constituting the tongue 50. Relative angular motion occurs between).

Accordingly, the guide washer 5 has a corrugated shape and includes a region 58 and a tongue 50 which constitute a dished concave region axially offset with respect to the tab in the direction of the piston 2, and the piston Is recessed in the shape of a dish below the area interacting with the friction lining 21 to fit the shape of the friction damper.

The tabs 41, 51 are adjacent but in contact and connected together by means of fastening means 11, and spot welding is performed at the center of the tabs 41, 51. The tab 41 is a reinforcing tab of the tab 51.

As a variant, the fixing is carried out by joining, riveting, bolting or any other mechanical means.

Of course, the washers 4, 5 can be fixed or fixed to one another at different points.

Lug 51 is provided with a 90 ° lateral fold 59. The tab 51 thus has a U-shaped cross section and forms a tenon that is complementary to the groove 22 provided in the axial annular skirt 23. The annular skirt 23 is formed on the outer circumferential portion of the piston 2. The skirt 23 is axially directed towards the guide washer 4 and towards the turbine wheel.

In this way, a rotatable engagement portion 51, 22 is formed between the guide washers 4, 5 and the piston 2. This engagement allows the axial movement of the piston opposite the tab 51 and the torsional damper 3. Fold 59 interacts with the lateral edge of axial groove 22.

The skirt 23 thus takes the form of an annular comb, the axial length of which depends on the application.

It will be noted that good relative motion of the piston 2 is achieved because the fold 59 is flexible and gentle, unlike roughening by cutting the lateral edges of the grooves 22.

Of course, the fold 59 is longer in the axial direction than the thickness of the guide washer 5. In this way, the phenomenon of covering the tab 51 at the edge of the groove 22 is limited.

Thus, the contact area between the lugs 51 and the edges of the grooves 22 is increased, so that the risk of pinching of the piston 2 is reduced and the slide of the piston is promoted in a reliable and continuous manner. This is true in most cases because the fold 59 is elastic.

The tab 41 on the other guide washer is coupled to the U-shaped tab 51. According to one feature of the invention, the thickness of the tab 41 is preferably shorter than the axial length of the fold 59, and there is a circumferential play between the lateral edge of the tab 41 and the fold 59. This is preferable because the entire fold 51 is gradually elastically engaged with the lateral edges of the grooves 22 forming the tenon holes. The fold 59 is elastic and thus elastically deformable. Fold 59 has a height greater than the thickness of reinforcing tab 41.

The reinforcing tab 41 prevents the fold 59 from plastically deforming, so that the play between the tab 41 and the fold 59 is determined. Thus, the entire tab 51 will deliver torque.

The elasticity of the fold 59 makes it possible to reduce manufacturing tolerances, reduce noise and reduce stress.

The deformation of the fold 59 is supported by the fact that the tabs 41, 51 are fixed to each other by the fastening means 11.

Tabs 41 and 51 and tongues 40 and 50 have the same outer periphery.

Of course, the tab 51 is higher than the tab 41 to form the fold 59, so that the washers 4, 5 are asymmetric.

The torsional damper 3 is very dense in radial direction by the circumferential intersection of the tabs 41, 51 and the tongues 40, 50 which receive the third spring 7.

The tab 41 reinforces the tab 51 and thus a high strength tenon is achieved. Thus, the tab 41 is accommodated in the tab 51.

Of course, the fold 59 (see FIG. 5) may be thermally compressed at 150 to secure the tab 41.

The structure of the tabs 41, 51 is applicable to the torsional damper 3 with the damper plate 6 coupled to the guide washers 4, 5 by an elastic member. For this embodiment, the presence of the switching ring is not essential.

Similarly, in the stop position (torque is not transmitted) of the torsion damper 3, the arm 60 is disposed symmetrically on the scallop 86.

Of course, the arm 60 may be arranged asymmetrically.

Likewise, the resilient members 70, 71 can be composed of concentric springs of different lengths.

For example, the elastic members can include three concentric springs of different lengths.

All members follow the characteristic curve that they want to achieve, which curve is asymmetrical, pulled or retracted in direction, and the engine drives the car wheel in the first case (pull direction), while in other cases ( Return direction) to drive the engine.

Torsion dampers may form part of the friction disk. In this case, the damper plate is fixed to a fluted hub to rotatably couple it to the input shaft, while the guide washer is formed on the outer circumference of the friction disk.

In general terms, the torsional damper acts between the first torque transmission element (piston 2) and the second transmission element (hub 106) in a driven or driven manner. The shape of all dampers mentioned in French Patent Publication No. 2 393 199 mentioned above can be assumed.

The tab 51 may take other shapes to promote deformation of the fold of 90 °.

Thus, the fold 59 is connected to the rim 159 protruding from the main part of the tab 51 as shown in FIG. In this way, it is possible to increase the length of the fold and its flexibility.

The holes 53 and 54 form not only the scallop 85 of the elastic member but also the housing.

As a variant, these housings 53, 54 can take other shapes and can be configured, for example, in a dish shape. In addition, the tongue 40 may be formed in a dish shape.

The number of tabs 41, 51 depends on the application, in particular the torque to be delivered.

The size of the dish-shaped regions 58, 50, 58 depends on the application, in particular the relative angular movement between the guide washers 4, 5 and the diverting ring 8.

In FIG. 5 the fold 59 prior to folding may be shown in dashed lines, providing a portion of reduced thickness in the fold to form the thermal crimp 150.

To this end, the tab 151 is formed by a semi-circular scallop 152. The tab 151 is deformed to secure the tab 41 to the tab 51 by crimping. The tab 51 is higher than the tab 41 to form the fold 59 as shown in FIG. 5.

2 shows, in part, a dashed line, one of the lateral edges of the lug 81 immediately before contacting the shoulder 10 at the end of the angular motion.

Of course, the third elastic member 7 may have a hardness equal to or close to that of the other elastic member.

Arm 60 may have a 90 ° fold similar to tab 51 such that the fold of arm 60 replaces stud 83.

According to the present invention, the torsional damper 3 can have three pairs of elastic members 70 and 71 and three holes since it is possible to attain a high torque after all. The spring 7 may alternatively be mounted freely in the hole 84 and may be mounted freely in the hole 54.

Fold 59 may be powerful such that a small number of tabs 51 may participate in the transmission of torque.

The tab 51 is axially offset relative to the dish-shaped regions 58 and 50 so that the bottom of the groove in the skirt 23 can be positioned away from the transverse portion of the piston as shown in FIG. 1. You will be aware.

Thus, the skirt 23 is strong and a large material of the ring exists between the lower part of the groove 22 and the rounded area, which rounded the skirt 23 of the piston 2 with friction lining 21. Connect to the horizontal part.

Of course, four lugs 81 and tongues 40, 50 can be provided. In this case, four springs 7 are present.

The first pair of springs 7 can be mounted in the hole 84 with a different clearance than the second pair of springs 7. Thus, some springs 7 can be operated in an extended manner.

Of course, the fold 59 on the tab 51 may belong to a torsional damper without a switch ring. Thus, the lug 81 forms a part of the damper plate 6 as a variant, and the shift ring, the lower part of the guide washers 4 and 5 and the springs 70 and 71 are omitted.

Claims (14)

And two coaxial parts 4, 5, 6 mounted angularly with respect to each other as opposed to the first and second groups of elastic members 70, 71 mounted in series by a switching ring 8, The switching ring is interposed between the first elastic member in the elastic member 70 of the first group and the second elastic member in the elastic member 71 of the second group, respectively, and the radially directed projection 80 Wherein one of the two coaxial parts has a damper plate 6 with a radially facing arm 60 for cooperating with the first and second elastic members 70, 71, while the other The coaxial component has two guide washers 4, 5 arranged on each side of the damper plate 6 and the diverting ring and the first elastic member 70 and the second elastic member 71. Torsional dampers of hydrodynamic coupling devices, each having a housing 53 for mounting In, Coupling means are provided between the arm 60 of the damper plate 6 and the diverter washer 8, and a third group of circumferentially acting elastic members 7 is provided with the guide washers 4, 5. Between the switching rings 8, the third group of elastic members 7 on one hand over the first and second groups of elastic members 70, 71 and on the other hand with a play 9. Characterized in that it is arranged radially on the coupling means having Torsional dampers in hydrodynamic coupling devices. The method of claim 1, The engaging means with the clearance 9 is characterized in that it forms a first stop and a molded part of the divert ring 8. Torsional dampers in hydrodynamic coupling devices. The method of claim 2, The shoulder 83 is characterized in that to define the projections (85) each having a projection (80) laterally Torsional dampers in hydrodynamic coupling devices. The method of claim 3, wherein Each arm 60 is mounted to a scallop 86 defined by two successive protrusions 85. Torsional dampers in hydrodynamic coupling devices. The method of claim 3, wherein The arms 60 each have circumferential studs 63 laterally on their outer periphery, the circumferential studs forming a reverse stop which forms part of the engaging means having the play 9 and the shoulder ( 83) suitable for interaction with Torsional dampers in hydrodynamic coupling devices. The method of claim 1, The third elastic member 7 is mounted facing each other in the housings 84 and 54 which are formed facing each other in the lug 81, the tongues 40 and 50 respectively being the shifting ring 8 and the guide washer 4. , 5), wherein the lugs 81 and the tongues 40, 50 are formed in radial projections at the respective outer periphery of the diversion ring 8 and the guide washers 4, 5. Torsional dampers in hydrodynamic coupling devices. The method of claim 6, The third elastic member 7 is characterized in that it is mounted floating on the lug 81 and the opposing housings 84, 54 in the tongues 40, 50. Torsional dampers in hydrodynamic coupling devices. The method of claim 6, One of the tongues 40, 50 belongs to at least an axially dished area 58, 50 for the formation of the shoulder 10, the shoulder being the shifting ring 8 and the guide washer 4, 5) forming a second stop limiting the relative angular movement therebetween, wherein the dish-shaped regions 58, 50 are arranged radially over the joining means having the play 9; Torsional dampers in hydrodynamic coupling devices. The method of claim 8, The guide washers 4, 5 are provided with radial projections on their outer circumferences and are in contact with each other in contact with the tabs intersecting the lugs 81 and the tongues 40, 50. Torsional dampers in hydrodynamic coupling devices. The method of claim 9, The tabs 41 and 51 are narrower in the circumferential direction than the lug 8 and narrower in the circumferential direction than the tongues 40 and 50. Torsional dampers in hydrodynamic coupling devices. The method of claim 9, The lug 51 on one of the guide washers referred to as the first tab 51 receives a fold 59 at 90 ° for receiving a tab 41 called the second tab 41 on the other guide washer 4. Characterized in that provided on the side Torsional dampers in hydrodynamic coupling devices. The method of claim 11, A play is present between the second tab 41 and the fold 59. Torsional dampers in hydrodynamic coupling devices. The method of claim 1, The first tab 51 defines a tenonal hole which is joined in a complementary manner to the groove 22, which groove is an axial annular skirt 23 on the piston of the lockup clutch 1 of the hydrodynamic coupling device. Characterized by belonging to Torsional dampers in hydrodynamic coupling devices. The method of claim 1, The hardness of the elastic member in the elastic member 7 of the third group is greater than the hardness of the elastic member 70 of the elastic member 70 of the first group and the elastic members 70 and 71 of the second group. Torsional dampers in hydrodynamic coupling devices.