KR20160096088A - Pendulum torsion damping device with improved effectiveness of filtration - Google Patents

Abstract

The present pendular torsional damping device intended to be connected to the internal combustion engine of the main order N includes a vibrating weight movably mounted on the support. The local order OR of the pendulum is adjusted downward and is substantially lower than N over the pendulum displacement range DBT close to the maximum displacement C ***. This device allows to obtain effective pendulum damping which reduces pendulum saturation phenomenon at low engine speed without causing saturation phenomenon at high engine speed.

Description

TECHNICAL FIELD [0001] The present invention relates to a pendulum torsion damping device having improved filtering effect,

The present invention relates to a pendulum oscillator type torsion damping device intended to be connected to an internal combustion engine.

In particular, pendular torsional damping devices, also known as pendulum oscillators or pendulums, which are installed in, but not limited to, transmissions of automobiles, are known in the art.

In a transmission of an automobile, at least one torsional damping is applied to a clutch capable of selectively connecting an engine to a gear box, such as a hydrodynamic coupling device or friction clutch, which includes a lockup clutch to filter out vibrations due to irregular rotation of the engine. Connect the device.

Indeed, the internal combustion engine exhibits irregular rotation due to continuous explosion in the engine cylinders, and this irregular rotation is particularly dependent on the number of cylinders.

Therefore, the damper means of the torsion damping device has a function of filtering the vibration generated by the irregular rotation and intervenes before the engine torque is transmitted to the gear box.

Otherwise, vibrations infiltrate the gearbox, causing shock, noise or particularly undesirable noise pollution when operating there.

For this reason, one or a plurality of damping means capable of filtering the vibration having at least one predetermined frequency is used.

Document US-2010/0122605 discloses a pendulum type damping device.

The damping device includes at least one support rotatably connected to the engine shaft and at least one vibrating weight, generally a plurality of vibrating weights circumferentially distributed on the support. The vibration of these vibrating weights generates a vibration torque that absorbs a part of the irregular rotation of the engine against the vibration torque coming from the engine. The support of the vibration weight of the torsion damping device is typically integral with the engine shaft.

Each vibrating weight is generally comprised of a pair of counterweights disposed on both sides of the support and typically integrally coupled to each other via a mechanical connection or a spacer directly across the cutout of the support. Hereinafter, these two counterweight assemblies, which are integrally combined with each other with or without a spacer, are regarded as one vibration weight.

Alternatively, each vibrational weight may be a unique counterweight that is movably mounted on the support. The support is in this case optionally formed by two elements, and vibrational weights can be movably arranged between the two elements.

These oscillating weights are very commonly mounted on a support by means of at least one rolling bearing element, typically two or more rolling bearing elements.

Typically, the center of mass of each vibrating weight oscillates freely about an oscillation axis substantially parallel to the rotation axis of the engine shaft, and rotates about the rotation axis.

In response to rotation irregularities, the oscillating weight is displaced such that the center of mass of each of these oscillating weights is oscillated about the oscillation axis. Hereinafter, the terms "torsion damping device" and "pendulum"

Includes a single rolling bearing element per oscillatory section called "monofilar pendulum" using a pendulum including two rolling bearing elements (or rollers), typically referred to as a "bifilar pendulum" A damping performance superior to the damping performance of the pendulum can be obtained.

Thus, during pendulum movement, each vibrational weight of the pendulum vibrates with (substantially different) left and right displacements about a neutral position inherent to this weight. This neutral position corresponds to the equilibrium position when the pendulum is driven at a constant speed which is sufficiently uniform to be driven outward in the radial direction by the oscillating additional centrifugal force.

On the one hand the center of mass and, on the other hand, the respective rolling bearing elements, the associated vibrational weight and the contact points of the support vibrate about the neutral point corresponding to the neutral position, respectively. The pendulum displacement out of the neutral position typically corresponds to the abscissa (x) of the center of mass in a predetermined vertical direction (e.g., in the rotational direction of the pendulum) with respect to the radial direction through which the mass center passes at the neutral position. Each value of the pendulum displacement corresponds in one-to-one fashion to the abscissa of the rolling bearing element and the support on the one hand and to the abscissa of the respective contact point of the rolling bearing element and the oscillating weight on the one hand, In the same manner as described above. Therefore, the predetermined pendulum displacement range (at the center of mass) corresponds to the range of change of the abscissa of the contact point between the rolling bearing element and the vibration weight or the support in a one-to-one manner.

The radial position of the center of mass of each oscillation shaft with respect to the rotational axis of the engine shaft as the distance of the center of mass with respect to the oscillation axis is set such that the frequency of oscillation of each oscillation weight is proportional to the rotational speed of the engine shaft under the action of centrifugal force, Is set to be close to the dominant harmonic order of the irregular rotation, for example.

The pendulum is calculated to fit the number of revolutions per revolution associated with the combustion in a given internal combustion engine, particularly the cylinder of this engine. Thus, typically, the order N of the internal combustion engine is defined as one half of the number of cylinders of the engine. Thus, for an engine comprising one to twelve cylinders, N may vary from 0.5 to 6, and has a value of 2 for an engine having four cylinders, for example, generating two cycles per revolution.

Therefore, the pendulum connected to this engine must be adjusted to the order of the engine, and the industry rules are that it is very close to the order N of the engine, generally slightly exceeding this in view of the aging wear of the pendulum system, For example to guide the pendulum weight and the rolling track on the support precisely in order to obtain an order of pendulum of N x 1.04 (this term will be explained in the following description of Fig. 1).

However, the damping of irregular rotation is not always perfect and it has been found that there is a very frequent engine system that causes pendulum saturation problems for irregular rotation filtering.

It is known from the application DE 10 2011 076 790 to construct a pendulum such that the order of the pendulum is lower than the order of the engine.

Pendulums are known from which the order can be changed from the application DE 10 2011 085 400.

One of the objects of the present invention is to limit or suppress such pendulum saturation phenomenon.

For this purpose, the object of the invention is a bipyrator-type pendulum torsional damping device intended to be connected to an internal combustion engine of main order N, the device comprising a support rotatably movable about a rotation axis and a pendulum Each vibrating weight of the assembly being able to oscillate on two rolling bearing elements which are connected to the vibrating weight and which are in rolling contact with the vibrating weight and the support, Defining trajectories on edges of the weights and on the edges of the supports, each of which is associated with a left pendulum displacement and a right pendulum displacement on either side of a neutral position,

Each of these vibration weights and the locus on the support,

The local order of this pendulum assembly is a maximum value of 0.99 x N or less, preferably 0.98 x N or less, or 0.96 N or 0.95 N or less, or a predetermined percentage, in particular 50%, of the left-most pendulum displacement defined by G1max A left first pendulum displacement range beyond the position that indicates;

The local order of the pendulum represents a predetermined percentage, in particular 50%, of the right-most pendulum displacement defined by a maximum value of not more than 0.99 x N, preferably not more than 0.98 x N or 0.96 N or not more than 0.95 N, The first pendulum displacement range is located on the right side of the first pendulum displacement range,

At the left or right predetermined pendulum displacement position, the local order or OP _local of this oscillating weight assembly is typically defined as:

For any rolling bearing element in contact with the oscillating weight, the same local order for each rolling bearing element is characterized by:

Wherein:

- R _g is the distance between the mass center of the oscillating weight and the rotational axis;

- R _bp is the radius of curvature of the locus on the support at a point of contact with the rolling bearing element,

- R _m1 is the radius of curvature of the locus on the vibration weight at a point of contact with the rolling bearing element,

- r _bp is the radius of curvature of the rolling bearing element at a point of contact with the support,

- r _m is the radius of curvature of the rolling bearing element at the point of contact with the vibrating weight.

According to the present invention, by virtue of the fact that the pendulum torsional damping device (or pendulum) has left and right pendulum displacement ranges beyond the intermediate pendulum displacement with a relatively small order adjusted downward with respect to the engine order N, It is possible to reduce or suppress the saturation of the pendulum with respect to the large pendulum displacement corresponding to the irregular rotation in the pendulum.

According to a first embodiment of the device according to the invention, over the left and right pendulum displacement total amplitudes, the local order is 0.99 x N or less, preferably 0.98 x N or less, and very preferably the interval [0.70 N; 0.98 N], or even a gap [0.74 N; 0.96 N], or even in the interval [0.76 N; 0.95 N]. Although this causes incomplete adaptation of the pendulum to a relatively small pendulum displacement (corresponding to a relatively increased engine speed), this incomplete adaptation does not induce saturation of the pendulum, It was confirmed to be effective for filtering.

The local order may be substantially constant over the entire amplitude of the left and right pendulum displacements. This trajectory configuration makes it possible to use a constant radius of curvature (trajectory forming a circle part), which is relatively easier to use in the production of a pendulum than the trajectory of a variable radius of curvature.

According to a second embodiment of the present invention, each of these vibration weights and the locus on the support,

A left second pendulum displacement range starting from the neutral position and extending below the left first pendulum displacement range, wherein the local order is defined by a minimum value of 0.95 N or greater, less than 1.10 N, or G2min;

- the right side second pendulum displacement range starting from the neutral position and extending below the right first pendulum displacement range, wherein the local order is defined by a minimum value of not less than 0.95 N, less than 1.10 N or D2min, ,

- G1max is less than G2min, 2% to 30% of G2min, preferably 3% to 25% of G2min;

- D1max is less than D2min, 2% to 30% of D2min, preferably 3% to 25% of D2min.

Therefore, for a relatively low engine rotational speed corresponding to a relatively increased pendulum displacement, the radius of curvature of the locus is relatively increased and the local order (OP _local ) is relatively small, so that the saturation effect of the pendulum is reduced or suppressed . This corresponds to the left and right first pendulum displacement ranges.

Conversely, for a relatively increased engine rotational speed corresponding to a relatively small pendulum displacement, the radius of curvature of the locus is relatively small and the local order (OP _local ) is relatively increased, leading to good filtering of the irregular rotation. This corresponds to the left and right second pendulum displacement ranges.

The left first pendulum displacement range may be the same as the right first pendulum displacement range. For the neutral point corresponding to the neutral position, the left second pendulum displacement range may be the same as the right second pendulum displacement range.

The left or right first pendulum displacement range is preferably a pendulum displacement interval of 10% to 49%, preferably 15% to 35% of the total spacing of the left or right pendulum displacement, to the left or right maximum displacement position .

The left or right second pendulum displacement range extends from the neutral position to a pendulum displacement interval that is preferably 50% to 90%, preferably 65% to 80% of the total spacing of the left or right pendulum displacement.

The left or right first and second pendulum displacement ranges are advantageously separated by a transition range for the local order, preferably the local order by a continuous transition range.

According to a preferred aspect of the second aspect of the present invention, the ratio of the local order at the left or right maximum displacement point to the local order at the left or right neutral position is less than the interval [0.70; 0.95], preferably the interval [0.80; 0.90], the left or right local order changes from a neutral position to a left or right maximum pendulum displacement position in a non-decreasing or decreasing manner, preferably substantially continuously.

According to a third embodiment of the present invention, the local order is drastically reduced from the neutral position to the left or right maximum pendulum displacement position.

Advantageously, with respect to each oscillation weight, a curve portion representing a change in the radius of curvature of the path of the center of mass (CM) in the left or right first pendulum displacement range as a left or right direction function is a clothoid portion And the left or right direction is taken along the waterline along the radial direction through which the center of mass (CM) position passes in the neutral position.

According to the second and third embodiments, the local order changes. In other words, the pendulum displacement has at least two distinct values.

Finally, another object of the present invention is a single clutch, dual clutch or multiple clutch including a torsion damping device as defined above.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood by the following detailed description which is given by way of example only with reference to the accompanying drawings, in which:
BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is an axial view, simplified in part, of a prior art torsion damping device belonging to a clutch, including a support and a vibrating weight mounted on the support at a neutral position,
Figure 2 is a view similar to that of Figure 1, showing that the damping device is in a different operating configuration corresponding to the left maximum displacement position,
Figure 3 is a simplified illustration of a portion of a pendulum to precisely define the parameters of a local order of a pendulum,
Fig. 4 shows the right three trajectories of a vibration profile, one corresponding to the prior art and the other two corresponding to the first and second embodiments of the present invention, respectively; Fig.
Fig. 5 is a diagram showing a change in radius of curvature of the locus shown in Fig. 4,
Fig. 6 is a diagram showing a change in the order of the vibration weight corresponding to the trajectory of Fig. 4,
7 is a diagram showing a change in order of a vibration weight for an apparatus according to a third embodiment of the present invention,
8 is a diagram showing a change in radius of curvature of a locus for an apparatus according to a third embodiment of the present invention,
Figure 9 shows an embodiment variant in which blocking of rolling bearing elements can be prevented,
Fig. 10 is an enlarged view of a part of Fig. 9,
11 shows the path of the center of mass (CM) of the oscillating weight during vibration-induced oscillation for the device according to the fourth embodiment of the present invention,
12 is a view showing a change in the radius of curvature of the curve of Fig. 11;

Referring now to Figure 1, there is shown in Figure 1 a partial schematic view of a torsion damping device 2 comprising a support 4, which comprises a plurality of circumferentially distributed pendulum oscillations And a circumferential portion having a general shape of an annular plane which is additionally movably installed. In Fig. 1, only two spacers 6 for connecting two counter wafers belonging to the same oscillation weight are shown, and these two counter wavers are arranged on both sides of the support body 4. Fig. The two counter waiter and the spacer 6 belong to the same oscillation weight.

The oscillating weight rolls on the support 4 by means of two rolling bearing elements 8 which each extend in the cutting of the contour 10 in the support 4. [ The vibrating weight is shown in Fig. 1 as a neutral position, and the contact point between the weight and each rolling bearing element is the center point (NE).

In Figure 1, the rolling contact of the oscillating weight with the support 4 connected at the spacer 6 is shown. In another configuration, the rolling contact may be in these two counter wavers, rather than in a spacer that joins two counter wavers.

In addition, the pole C of the rightward trajectory is shown (relative to the neutral point), and the right trajectory is the rolling bearing (between neutral points) between the neutral point and the contact point at the left- (NE-C) corresponding to the set of contact points of the element.

This left maximum displacement position of the weight is shown in FIG. 2, in which the spacer 6 of the oscillating weight is displaced to the left with respect to the support as compared to the neutral position of FIG.

The displacement or pendulum displacement is the distance between the position of the center of mass of the oscillating weight and the position of this center of mass at the neutral position.

In a similar manner, it defines trajectories on the support corresponding to the set of contact points of the rolling bearing element and the support, respectively.

All vibrational weights typically have the same loci on the left (of neutral points) and the same right trajectory on the right (of neutral points) for the two rolling bearing elements, for two rolling bearing elements. Conversely, the right trajectories may be different from the left trajectories.

The same is true for the trajectories on the support.

Reference is now made to Fig. 3, which shows the trajectories 12 on the vibrational weight and the trajectories 14 on the support in a more general way.

Fig. 3 corresponds to a pendulum configuration different from the pendulum configuration of Figs. 1 and 2, in which the rolling bearing element 8 comprises a first section 16 of radius of curvature _{rm in} contact with the oscillating weight, And a second section 18 of radius of curvature r _bp . Figures 1 and 2 correspond particularly to the case where r _m = r _bp . The CR point represents the center of rotation through which the axis of rotation of the pendulum passes (distance not shown).

The local order or OP _local of the pendulum at a given location is typically defined by the following equation:

Wherein:

- R _g is the distance between the mass center of the oscillating weight and the rotational axis;

- R _bp is the radius of curvature of the locus on the support at a point of contact with the rolling bearing element,

- R _m1 is the radius of curvature of the locus on the vibration weight at a point of contact with the rolling bearing element,

- r _bp is the radius of curvature of the rolling bearing element at a point of contact with the support,

- r _m is the radius of curvature of the rolling bearing element at the point of contact with the vibrating weight.

Referring now to Fig. 4 which shows the right three trajectories of the vibration profile, one trajectory corresponds to the pendulum according to the prior art and the other two trajectories correspond respectively to the first and second embodiments of the pendulum according to the invention, .

The rightward direction represented by the abscissa (x) is considered along the waterline along the radial direction through which the position of the neutral point of the locus passes, corresponding to the neutral position with respect to the pendulum displacement. The ordinate axis y starts from the neutral point NE and extends along the radial direction. Since all right trajectories in different weights are equal to each other and are assumed to be the same as the left trajectories in these weights, the same is true for the trajectories in the support.

The upper trajectory corresponding to the right first trajectory: point NE (neutral point), M (intermediate transverse coordinate point), A, and C has a substantially uniform radius of curvature R and a conventional trajectory with order OM = (Right side), and the local order or OR corresponding to the pendulum is constant and is generally close to 2.04. These pendulums appeared satisfactory at intermediate engine speeds and increased engine speeds, but were not able to meet the sudden acceleration filtering capability at low engine speeds, typically below 1500 rpm in strong acceleration during saturation.

Right Second Trajectory: Dotted line locus NE-C * corresponding to the pendulum according to the first embodiment of the present invention is substantially uniform although the radius of curvature of the locus is also substantially equal, but the corresponding local order is constant Is substantially less than 2.04, such as 1.8. Thus, the order of the pendulum (or of the assembly of the oscillating weight) is adjusted downward with respect to the order of the two-engine. As a result, at low engine speeds corresponding to relatively increased pendulum displacement, the pendulum has a much lower or zero saturation range. However, on the other hand, its operation at intermediate engine speeds and engine speeds, which are comparatively small pendulum displacements, was surprisingly slightly lower than conventional pendulums of a homogeneous order of 2.04, indicating that pendulum saturation was not observed.

Therefore, this first embodiment of the bipyramidal pendulum torsion damping device (or of the pendulum) according to the present invention can significantly reduce or suppress the pendulum saturation phenomenon.

The right third trajectory (center) corresponding to the NE, M, A, B, and C ** points corresponds to the second embodiment of the present invention:

The portion NE-A of the locus has a radius of curvature R and is identical and common to the corresponding portion of the first locus according to the prior art.

Conversely, the end portion or B-C ** of this locus has a radius of curvature (R1 > R). As a result, from the neutral position (NE) corresponding to the zero displacement, the assembly of the pendulum (or oscillating weight) at this end portion corresponding to the left first pendulum displacement range (the left displacement corresponds to the right trajectory portion on the vibration weight) Order is smaller than the order in the call (NE-A) corresponding to the left second pendulum displacement range.

Thus, the left second pendulum displacement range extends below the left first pendulum displacement range from the NE point at the neutral position. In this second range, the local order is 2.04, so it is limited by the minimum value (G2min) of 0.95 N to less than 1.10 N (where N = 2).

The left first pendulum displacement range extends between point B and point C ** where the local order P of the oscillating weight assembly (advantageously all the oscillation weight of the pendulum) is limited by the maximum value or Glmax = 1.7 .

Between point A and point B, the radius of curvature R2 (x) increases along the abscissa x in such a way as to ensure a continuous transition between the left first pendulum displacement range and the left second pendulum displacement range.

The operation of the pendulum is improved compared to the first embodiment:

For a relatively low engine rotational speed corresponding to a relatively increased pendulum displacement, the radius of curvature of the locus is relatively increased and the local order (OP _local ) is relatively small, so that the pendulum saturation effect is reduced or suppressed.

- Conversely, for relatively higher engine rotational speeds corresponding to relatively small pendulum displacements, the radius of curvature of the locus is relatively small and the local order (OP _local ) is relatively increased, leading to better filtering of the irregular rotation.

Reference is now made to Figs. 5 and 6. 5 shows the change of the radius of curvature of the locus of FIG.

In the right first trajectory (upper curve in Fig. 4) corresponding to the prior art, the radius of curvature is constant and equal to R. [

In the right second trajectory (lower dotted curve in Fig. 4) corresponding to the first embodiment of the present invention, the radius of curvature is constant and equal to R1 (R1 > R).

In the right third locus (center) corresponding to the second embodiment of the present invention, the radius of curvature starts from the neutral point NE to the point A, as in the prior art (upper right locus of FIG. 4) And then has a value R2 (x) that increases in the transition zone between A and B to reach a constant value R1 up to the left maximum displacement point (C **) and maintain this value. Thus, the radius of curvature has a first value R starting at the neutral point NE and then has a further increased value R1 towards the left maximum displacement point C ** after the transition zone.

In this embodiment:

The left first pendulum displacement range corresponds to the B-C ** locus portion;

The left second pendulum displacement range corresponds to the NE-A locus portion.

Similar characteristics are generally used for the left trajectory on the right and left trajectories on the support and on the traces corresponding to the right pendulum displacement. Each of these trajectories is different in a first pendulum displacement range (relatively increased radius of curvature, relatively small local order) and a second pendulum displacement range (relatively small radius of curvature, relatively increased local order), generally defined in a similar manner And has a radius of curvature.

Fig. 6 shows the change of the order of the vibration weight corresponding to the locus of Fig. 4 according to the displacement DBT.

For the right first trajectory (top) of FIG. 4 corresponding to the prior art, the local order OP _local is constant and is 2.04 to point C.

In the right second locus (lower dotted line in Fig. 4) corresponding to the first embodiment of the present invention, the local order OP _local is constant and is 1.7 up to point R1 (where R1> R).

In the right third locus (center) corresponding to the second embodiment of the present invention, the local order OP _local starts from the neutral point NE, as in the prior art (upper right locus in FIG. 4) And then decreases in the transition zone between A and B to reach a constant value of 1.7 to the left maximum displacement point (C **) and maintain this value.

The left maximum displacement points C, C *, and C ** corresponding to different right trajectories in the considered weight may have the same abscissa x or have different abscissa.

7 shows a change in the order of the vibration weight according to the displacement DBT, with respect to the device according to the third embodiment of the present invention.

In this third embodiment, the local order OP _local is continuously reduced from the conventional value of 2.04 to the value 1.7 at the neutral point.

Correspondingly, the radius of curvature decreases continuously from the neutral point NE to the maximum displacement point C *** as shown in Fig.

The third embodiment allows much better pendulum adaptation. As the abscissa (x) and the displacement (DBT) increase (which corresponds to the rotational speed reduction), the radius of curvature increases and the local order (OP _local ) decreases in correlation, It is well adapted.

Figs. 4 to 8 disclose the right trajectories in the vibration weight, i.e., the trajectories of the contact points of one of the vibrating weight and the rolling bearing element. The same characteristics and similar curves appear for the left trajectories in the weights or the right trajectories in the support or the left trajectories in the support.

Reference is now made to Figs. 9 and 10 which show an embodiment variant which can prevent blocking of the rolling bearing element 8 relative to the pendulum partially shown in Figs. 1 and 2. Fig. Fig. 10 is an enlarged view of a part of Fig.

(Or C **, or C ***) on the vibration weight (here, on the spacer 6) to prevent the possibility of one or more rolling bearing elements deviating beyond the maximum displacement point Extend the rolling track. Such a configuration may appear particularly when the engine is started, when the vibration is no longer subjected to centrifugal force.

The extension of the actual trajectories corresponds to a call CD. The radius of curvature of these extensions may advantageously be between 8 and 1.5 times the diameter (DIA) of the rolling bearing element 8 to this diameter (DIA).

When the vibrating additional spacer 6 is in the radially inner stop position (point T in contour 10) (as shown in Figures 9 and 10) by contact of a portion of the radially inner plane of the cut, the distance H1 , H2, and H3 design a vibration weight and a cut on the support so as to exhibit the following relationship:

H3 = H1 - H2 < DIA,

here:

H1 is the radial maximum height of the cutout of the contour through which the spacer passes;

H2 is the maximum radial height of the spacer,

The DIA is the diameter of the rolling bearing element 8 in contact with the spacer 6.

Thus, even in the transient state, the rolling bearing element 8 can not move beyond the spacer 6 to the right and can not be blocked at the right portions of the contour 10.

Reference is now made to Figs. 11 and 12 corresponding to a fourth embodiment of the present invention.

Fig. 11 shows the trajectory of the center of mass CM of the vibrating weight during vibration of the vibrating weight. One right trajectory is shown for the neutral position.

The rightward direction indicated by the abscissa (x) is considered along the waterline along the radial direction through which the position of the center of mass (CM) passes in the neutral position. The ordinate axis (y) extends along the radial direction through the center of mass at the neutral point.

Zone BC ** corresponds to the right first angular displacement range. Zone AB corresponds to the transition zone, and the zone between the zero lateral coordinate point and point A corresponds to the right second angular displacement range.

Fig. 12 shows a change in the radius of curvature of the right-side orbit of the center of mass CM. According to a fourth embodiment of the invention, the radius of curvature is constant in the second angular displacement range up to point A initially. This then begins to increase in the AB transition zone and further increases from the first angular displacement range to the right maximum displacement point (C **).

Most preferably, this curve is the chloroid portion between point A and point C **. Therefore, the curved portion indicating the radius of curvature R in the right first angular displacement range B C ** is also the closest portion.

Therefore, the change of the radius of curvature of the orbit of the left mass center is also generally the same.

It has been found that the risk of sliding the rolling bearing element 8 on the weight and / or support can be greatly reduced or suppressed.

More generally, those skilled in the art will be able to practice the invention in accordance with different embodiments or variants known from the prior art compatible with the present invention without departing from the scope of the present invention.

Claims (10)

A pivotal pendulum tamping damping device (2) intended to be connected to an internal combustion engine of a main order N, comprising: a support body (4) which rotates about a rotation axis and a pendulum vibration weight Wherein each oscillating weight of the assembly is capable of oscillating on two rolling bearing elements (8) connected to the oscillating weight and rolling contact with the oscillating weight and the support, each of the rolling bearing elements Defining a trajectory on the edge of the weight and on the edge of the support, each of the trajectories being associated with a left pendulum displacement and a right pendulum displacement on either side of a neutral position,
Each of these vibration weights and the locus on the support (4)
The local order of the pendulum assembly is beyond the position indicating a predetermined percentage, in particular 50%, of the left-most pendulum displacement defined by the maximum value of 0.99 x N or less, preferably 0.98 x N or less, or G1max, One pendulum displacement range;
- the right side first pendulum beyond the position indicating the predetermined percentage, in particular 50%, of the right maximal pendulum displacement defined by the local value of the pendulum equal to or less than 0.99 x N, preferably equal to or less than 0.98 x N, Displacement range;
- a left second pendulum displacement range starting from said neutral position, said local order extending below a left first pendulum displacement range defined by a minimum value of 0.95 N or more, less than 1.10 N or G2min;
Starting from the neutral position, the local order is configured such that there is a right second pendulum displacement range extending below a right first pendulum displacement range defined by a minimum value of 0.95 N or greater, less than 1.10 N, or D2min, wherein ,
- G1max is less than G2min, 2% to 30% of G2min, preferably 3% to 25% of G2min;
- D1max is less than D2min, 2% to 30% of D2min, preferably 3% to 25% of D2min;
The local order or OP _local of the oscillating weight assembly at the left or right predetermined pendulum displacement position is typically defined as:
For any rolling bearing element in contact with the oscillating weight, the same local order for each rolling bearing element is characterized by
Pendulum torsion damping device.

Wherein:
- R _g is the distance between the mass center of the oscillating weight and the rotational axis;
- R _bp is the radius of curvature of the locus on the support at a point of contact with the rolling bearing element,
- R _m1 is the radius of curvature of the locus on the vibration weight at a point of contact with the rolling bearing element,
- r _bp is the radius of curvature of the rolling bearing element at a point of contact with the support,
- r _m is the radius of curvature of the rolling bearing element at the point of contact with the vibrating weight. The method according to claim 1,
The left first pendulum displacement range is the same as the right first pendulum displacement range with respect to the neutral point;
And the left second pendulum displacement range with respect to the neutral point is the same as the right second pendulum displacement range.
Pendulum torsion damping device. 3. The method according to claim 1 or 2,
The left or right first pendulum displacement range extends to the left or right maximum displacement position with a pendulum displacement interval of 10% to 49%, preferably 15% to 35% of the left or right total pendulum displacement interval;
The left or right second pendulum displacement range extends from a neutral position to a pendulum displacement interval of 50% to 90%, preferably 65% to 80% of the left or right total pendulum displacement interval;
Characterized in that said left or right first and second pendulum displacement ranges are separated by a transition range for said local order, preferably said local order by a continuous transition range
Pendulum torsion damping device. 4. The method according to any one of claims 1 to 3,
The ratio of the local order at the left or right maximum displacement point to the local order at the neutral position is less than the interval [0.70; 0.95], preferably the interval [0.80; 0.90], the left or right local order changes from the neutral position to the left or right maximum pendulum displacement position in a non-incremental manner, preferably substantially continuously.
Pendulum torsion damping device. 5. The method of claim 4,
The local order is strictly reduced from the neutral position to the left or right maximum pendulum displacement position
Pendulum torsion damping device. The method according to claim 4 or 5,
For each oscillation weight, a curve portion representing the change in the radius of curvature of the path of the center of mass (CM) in the left or right first pendulum displacement range as a left or right direction function forms a chlorodeode portion, Direction is taken along the waterline along the radial direction through which the center of mass (CM) position passes in the neutral position
Pendulum torsion damping device. A pivotal pendulum tamping damping device (2) intended to be connected to an internal combustion engine of a main order N, comprising: a support body (4) which rotates about a rotation axis and a pendulum vibration weight Wherein each oscillating weight of the assembly is capable of oscillating on two rolling bearing elements (8) connected to the oscillating weights and rolling contact with the oscillating weights and the support, each of the rolling bearing elements Defining a trajectory on the edge of the weight and on the edge of the support, each of the trajectories being associated with a left pendulum displacement and a right pendulum displacement on either side of a neutral position,
Each of these vibration weights and the locus on the support (4)
The local order of the pendulum assembly is beyond the position representing a predetermined percentage, in particular 50%, of the left-most pendulum displacement, defined by a maximum value of 0.99 x N or less, preferably 0.98 x N or less, or G1max, First pendulum displacement range;
The local order of the pendulum lies beyond the position representing a predetermined percentage, in particular 50%, of the right-handed maximum pendulum displacement, defined by a maximum value, or D1max, of 0.99 x N or less, preferably 0.98 x N or less, A pendulum displacement range is present,
Wherein the local order has an interval [0.74 N; 0.96 N]
At the left or right predetermined pendulum displacement position, the local order or OP _local of this oscillating weight assembly is typically defined as:
For any rolling bearing element in contact with the oscillating weight, the same local order for each rolling bearing element is characterized by
Pendulum torsion damping device.

Wherein:
- R _g is the distance between the mass center of the oscillating weight and the rotational axis;
- R _bp is the radius of curvature of the locus on the support at a point of contact with the rolling bearing element,
- R _m1 is the radius of curvature of the locus on the vibration weight at a point of contact with the rolling bearing element,
- r _bp is the radius of curvature of the rolling bearing element at a point of contact with the support,
- r _m is the radius of curvature of the rolling bearing element at the point of contact with the vibrating weight. 8. The method of claim 7,
Over the entire amplitude of the left and right pendulum displacements, the local order is spaced [0.78 N; 0.92 N].
Pendulum torsion damping device. 9. The method according to claim 7 or 8,
Characterized in that the local order is substantially constant over the entire amplitude of the left and right pendulum displacements
Pendulum torsion damping device. Characterized in that it comprises a torsion damping device according to any one of the claims 1 to 9
clutch.

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