WO2015162386A1

WO2015162386A1 - Torque transmission device for a motor vehicle

Info

Publication number: WO2015162386A1
Application number: PCT/FR2015/051106
Authority: WO
Inventors: Michaël Hennebelle; Roel Verhoog
Original assignee: Valeo Embrayages
Priority date: 2014-04-25
Filing date: 2015-04-23
Publication date: 2015-10-29
Also published as: KR102418261B1; JP2017514078A; KR20160148538A; FR3020425A1; FR3020425B1; DE112015001985T5

Abstract

The invention relates to a torque transmission device for a motor vehicle, comprising a torque input element (7a), a torque output element (24), and at least one set of elastic members (10a, 10b) which are mounted between the torque input elements (7a, 7b) and output elements (24) and arranged in series by means of a phasing member (30). The torque output element (24) and the phasing member (30) comprise first (28a, 33a) and second (28b, 33b) end-stop means limiting the relative rotation thereof in two opposite directions of rotation (D, R), the torque input element (7a, 7b) and the phasing member (30) comprising third (34, 17b) and fourth (34, 16b) end-stop means limiting the relative rotation thereof in two opposite directions of rotation (D, R).

Description

Torque transmission device for a vehicle

automotive

The present invention relates to a torque transmission device for a motor vehicle.

Such a device generally comprises a torque input element, a torque output element, and elastic members mounted between the input and torque output elements and acting against the rotation of one of said input and output elements of torque relative to each other.

When the torque transmission device is LTD (Long Travel Damper) type, it comprises several groups of elastic members, the elastic members of the same group being arranged in series via a phasing member so the elastic members of each group deform in phase with each other.

It is known to improve the quality of the filtration obtained by means of such a transmission device by reducing the stiffness of the elastic members and / or by increasing the implantation radius of the elastic members.

The patent application FR 2 988 455, in the name of the Applicant, discloses a transmission device of the aforementioned type in which the input and torque output elements comprise first and second stop means limiting their relative rotation in two directions of opposite rotation, the torque input member and the phasing member having third and fourth stop means limiting their relative rotation in two opposite directions of rotation, the input and output torque elements comprise fifths. and sixth stop means limiting their relative rotation in two opposite directions of rotation.

In particular, the third and fourth stop means are formed in particular by radially extending projecting elements, each projecting element being formed on one of the guide washers, by stamping. Each projecting element thus comprises two opposite abutment faces extending radially.

Such protruding elements have a large radial dimension and, taking into account the available radial space requirement, require the elastic members to be placed on a relatively small implantation radius and require the creation of a cut-out in the connection zone of the guide washers. which reduces their behavior. This, therefore, affects the efficiency of vibration filtration and rotation acyclisms performed using the torque transmission device.

The invention aims in particular to provide a simple, effective and economical solution to this problem.

For this purpose, it proposes a torque transmission device for a motor vehicle, comprising a torque input element, a torque output element, and at least one group of elastic members mounted between the input elements and of torque output and acting against the rotation of one of said input elements and the torque output member relative to each other, the elastic members of this group being arranged in series by via a phasing member so that the elastic members of each group deform in phase with each other, the torque output member and the phasing member having first and second means for stop limiting their relative rotation in two opposite directions of rotation, the torque input member and the phasing member having third and fourth stop means limiting their relative rotation in two opposite directions of rotation, c characterized in that the third and fourth abutment means comprise at least one abutment stud formed on the phasing member or respectively on the torque input element, and at least one elongated slot in the form of an arc of a circle. formed on the torque input element or respectively on the phasing member, the stop stud being inserted into the housing and being able to bear against each end of said housing, the first, second, third, fourth stop means and the housing are arranged such that the input member and the output member are adapted to be in contact with the phasing washer in an extreme position.

It is thus possible to form the third and fourth abutments using a pad of small diameter, and therefore of small radial size. The width of the elongate housing, that is to say its radial dimension, can also be reduced. The implantation radius of the elastic members can thus be increased, with the effect of improving the quality of the filtration performed.

Depending on the position of the different stops, it is possible to control the angular displacement of each of these elements, in particular to limit the compression of the elastic members mounted between the torque input member and the phasing member, on the one hand, and between the phasing member and the torque output member, on the other hand.

It is also possible that at a certain position, for example in the extreme position, the path of the torque transits from a torque input to the torque output and vice versa through the phasing member via the first, second, third and fourth stop means.

Preferably, the elastic members are helical compression springs, and the abutment means are designed to limit the compression of the springs and prevent the turns of the springs come into abutment on each other.

In this way, the helical springs are prevented from being damaged by crushing their turns.

According to one characteristic of the invention, the elastic members of the or each group bear, on the one hand, on an annular web forming the torque output element, or respectively the torque input element and, d on the other hand, on two guide washers which extend radially on either side of the annular web and which are movable in rotation relative thereto, the guide washers forming the torque input member, or respectively the torque output member.

According to another characteristic of the invention, the phasing member comprises a radially outer annular portion, from which tabs extend radially inwards and serve to support the elastic members.

In this case, the stop stud may extend axially from the radially outer annular portion of the phasing member, facing one of said legs of the phasing member, that is to say in a zone having high mechanical strength.

Advantageously, the annular web comprises a radially inner annular portion from which support lugs of the elastic members extend radially outwardly.

Compared with an annular web having mounting windows of resilient members, the aforementioned annular web allows to place the springs on a circumference of larger diameter. This improves the filtration of vibrations and rotational acyclisms of the engine.

Furthermore, abutment means extend circumferentially on either side of each of the tabs of the annular web and the phasing member, so that the abutment means of the annular web are able to come into abutment. on the stop means of the phasing member.

Such a structure ensures a simple and reliable stop function between the phasing member and the annular web in both directions of rotation.

According to a feature of the invention, in an extreme position, the stop means extend circumferentially on either side of each of the legs of the annular web and the phasing member, so that means of abutment of the annular web are able to bear against the stop means of the phasing member, the stop stud being able to also bear against one end of the housing of the torque input element.

Thus, during a given position, for example in extreme position, it is possible for the path of the torque to pass from a torque input to the torque output and vice versa via the phasing member via the first, second, third and fourth stop means.

Preferably, the torque transmission device comprises two guide washers fixed to one another by riveting and / or welding at their radially outer periphery.

In this case, at least one of the guide washers may comprise, at its radially outer periphery, deformable tongues adapted to be folded down on the other guide ring so as to ensure their attachment to one another.

In addition, the torque transmission device may be a hydrodynamic torque converter.

The invention will be better understood and other details, characteristics and advantages of the invention will appear on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which:

FIG. 1 is a schematic view of a torque transmission device according to the invention, in the form of a hydrodynamic torque converter,

FIG. 2 is a perspective view in longitudinal section of part of a torque transmission device according to the invention,

FIG. 3 is a front view of a portion of the torque transmission device of FIG. 2,

FIG. 4 is a perspective view of part of the torque transmission device,

FIG. 5 is a perspective view of the annular web,

FIG. 6 is a perspective view of the phasing member, FIG. 7 is a perspective view illustrating one of the guide washers,

- Figures 8 to 12 are front views of a portion of the torque transmission device in several angular positions of the various moving elements.

A hydrodynamic torque converter according to the invention is shown schematically and partially in FIG. This converter makes it possible to transmit a torque of an output shaft of an internal combustion engine of a motor vehicle, such as for example a crankshaft 1, to an input shaft 2 of a gearbox.

The torque converter conventionally comprises an impeller impeller 3 capable of hydrokinetically driving a turbine blade wheel 4 via a reactor 5.

The impeller wheel 3 is coupled to the crankshaft 1 and the turbine wheel 4 is coupled to a turbine hub 6, itself coupled to two guide washers 7, hereinafter referred to respectively as the rear guide washer 7a and the washer front guide 7b.

The front guide ring 7b and the turbine hub 6 are rotatably mounted around a splined central hub 8, to be coupled to the input shaft 2 of the gearbox.

The front guide ring 7b is mounted around the turbine hub 6 and fixed thereto. The two guide washers 7a, 7b extend radially and delimit between them an internal space 9 housing elastic members 10a, 10b, which are for example helical compression springs.

The rear guide washer 7b has a cylindrical rim January 1 at its radially outer periphery, extending towards the front guide ring 7a and fixed thereto.

The free end of the cylindrical flange 1 1 comprises tongues 12 extending axially, before fixing the two guide rings 7a, 7b therebetween. These tongues 12 are folded on the outer periphery of the front guide ring 7a, during a riveting operation, and can be welded thereto, so as to ensure the fixing of the two guide rings 7a, 7b.

The guide washers 7a, 7b conventionally comprise windows 13 formed facing the elastic members 10a, 10b.

As illustrated in Figure 7, each guide ring 7a, 7b has three zones 14 projecting into the inner space 9, formed by stamping. Each zone 14 has two opposed and radial surfaces 14a, 14b, intended to support the elastic members 10a, 10b.

One of the guide washers 7a, 7b, here the rear guide washer 7b, further comprises three slots or slots 15, shaped circular arc extending at an angle of between 20 ° and 40 °, for example. The slots 15 are located radially outside the stamped areas 14 and windows 13 and radially inside the cylindrical flange January 1. Each light has two ends, referenced respectively 15a, 15b.

A splined hub 16 (Figure 2) is also attached to the rear face of the rear guide ring 7b. This splined hub 16 has a radial portion 17 fixed on said rear face of the rear guide washer 7b, and a fluted cylindrical flange 18 extending rearwardly from the radially outer periphery of the radial portion 17.

A clutch 19 (FIG. 1) makes it possible to transmit a torque from the crankshaft 1 to the guide washers 7, in a determined operating phase, without involving the impeller wheel 3 and the turbine wheel 4. This clutch 19 comprises an element inlet 20 coupled to the crankshaft 1 and an output member, including the splined hub 16.

An annular radially extending web 21 is mounted in the inner space 9 and is fixed on the central hub 8.

As best seen in FIG. 5, the annular web 21 has a radially inner annular portion 22 from which tabs 23, for example three in number, extend radially outwardly. Each lug 23 has two opposite faces 23a, 23b serving to support the elastic members 10a, 10b, inclined with respect to each other and with respect to the radial direction. Two abutment studs 24a, 24b extend circumferentially on either side of each tab 23, at its outer periphery.

The elastic members 10a, 10b are mounted circumferentially between the annular web and the guide washers 7a, 7b.

More particularly, the elastic members 10a, 10b are arranged in pairs. The elastic members (FIG. 1) of the same pair are arranged in series via a common phasing member 25, so that the elastic members 10a, 10b deform in phase with one another. In the embodiment shown in the figures, the torque converter comprises three pairs of elastic members 10a, 10b.

Thus, for each pair of elastic members 10a, 10b, depending on the direction of rotation of the guide washers 7a, 7b with respect to the annular web 21, one of the elastic members (for example 10a) is intended to bear, on the one hand, on one of the faces 14a, 14b of the corresponding projecting zone 14 of the guide washers 7a, 7b and, on the other hand, on the phasing member 25. The other elastic member (by Example 10b) is then intended to bear, on the one hand, on the phasing member 25 and, on the other hand, on one of the faces 23a, 23b of the corresponding tab 23 of the annular web 21.

FIG. 3 illustrates the case where the springs 10a are partially compressed by the relative rotation of the phasing member 25 and the annular web 21. At rest, the elastic members 10a and 10b have substantially the same length.

As best seen in Figure 6, the phasing member 25 has a radially outer annular portion 26, from which tabs 27 extend radially inwardly. Each leg 27 comprises two opposite faces 27a, 27b serving to support the resilient members 10a, 10b, inclined with respect to each other and with respect to the radial direction. The outer annular portion 26 has zones 28 of large width, that is to say of strong radial dimension, circumferentially located on either side of the tabs 27. These zones 28 serve to support the radial turns of ends of the elastic members 10a, 10b, in particular in operation, when the elastic members 10a, 10b are subjected to the centrifugal effect. This ensures that, in operation, the other turns do not come to rest and rub on the radially outer annular portion 26 of the annular web 25.

The circumferential ends of the zones 28 form shoulders or radial abutment surfaces, referenced 29a and 29b.

Cylindrical studs 30 also extend axially, facing each lug 27 and at the level of the radially outer annular portion 26.

In operation, the abutment studs 24a, 24b of the tabs 23 of the annular web 21 are able to bear respectively on the abutment surfaces 29a, 29b of the shoulders 28 of the phasing member 25. Moreover, in operation, the cylindrical studs 30 of the phasing member 25 are intended to bear against the ends 15a, 15b of the housing 15 of the guide ring 7b.

Moreover, the phasing member 25 can be coupled to pendular damping means 31, intended to improve the filtration of vibrations and rotational acyclisms, as illustrated in FIGS. 2 and 4. The pendulum damping means 31 comprise pendular masses 32 movably mounted on a support 33 coupled in rotation to the phasing member 25.

The pads 24a, 24b, the abutment surfaces 29a, 29b, the cylindrical studs 30 and the ends 15a, 15b of the housings are positioned and dimensioned so as to limit the compression of the elastic members 10a, 10b and to avoid, when acts of coil springs, that the turns of the springs are joined during their compression, whatever the mode of operation of the torque converter.

FIG. 8 shows the torque converter according to the invention in a position in which the pads 24a, 24b are spaced apart from the abutment surfaces 29a, 29b and in which the pads 30 are spaced apart from the ends 15a, 15b.

In a first case of operation illustrated in FIG. 9, the phasing member 25 pivots in a direction of rotation called retro direction (referenced by the arrow R in the figures) from the position illustrated in FIG. 8, with respect to the washers. guide 7a, 7b. The deflection of the phasing member 25 can then be limited by abutting the studs 30 on the ends 15b of the housing 15 of the guide ring 7b.

In a second operating case, illustrated in FIG. 10, the phasing member 25 and the annular web 21 can pivot relative to one another to an extreme position in which the pads 24a of the annular web 21 and the abutment surfaces 29a of the phasing member 25 abut one another. As indicated above, these studs 24a and these abutment surfaces 29a are positioned and dimensioned so as to limit the compression of the elastic members 10a, 10b. In the case shown in FIG. 10 also, the studs 30 can abut on the ends 15b of the housings 15.

FIG. 11 illustrates a third case of operation in which the phasing member 30 has pivoted in the direct direction (arrow D) from its position shown in FIG. 8, relative to the guide washers 7a, 7b, this pivoting being limited by abutment of the studs 30 on the ends 15a of the housings 15 of the guide ring 7b.

Finally, FIG. 12 illustrates a fourth case of operation in which the phasing member 25 and the annular web 21 can pivot relative to one another to an extreme position in which the pads 24b of the annular web 21 and the abutment surfaces 29b of the phasing member 25 abut one another. In the case also represented in FIG. 12, the studs 30 can abut on the ends 15a of the housings 15. The torque then travels from the annular web 21 to the guide washers 7a, 7b and vice versa via the phasing member 25. via the pads 24b, the abutment surfaces 29b, the pads 30 and the ends 15a of the housings 15.

The invention thus proposes a torque transmission device, for example in the form of a torque converter or a double damping flywheel, adapted to limit the rotation of the guide washers 7a, 7b with respect to the phasing member 25, the rotation of the annular web 21 with respect to the phasing member 25, and, indirectly, the rotation of the guide washers 7a, 7b with respect to the annular web 21.

Depending on the position of the different stops, it is possible to control the angular displacement of each of these elements, in particular to limit compression and prevent damage to the elastic members 10a, 10b mounted between the guide rings 7a, 7b and the phasing member 25, on the one hand, and between the phasing member 25 and the annular web 21, on the other hand.

Moreover, in comparison with the prior art, the invention also makes it possible to increase the radius of implantation of the elastic members, with the effect of improving the quality of the filtration performed.

Claims

1. Torque transmission device for a motor vehicle, comprising a torque input member (7a, 7b), a torque output member (21), and at least one group of elastic members (10a, 10b) mounted between the input (7a, 7b) and output (21) elements of torque and acting against the rotation of one of said input elements (7a, 7b) and the output element (21) of torque relative to one another, the elastic members (10a, 10b) of this group being arranged in series via a phasing member (25) so that the elastic members (10a, 10b) of each group deform in phase with each other, the torque output member (21) and the phasing member (25) having first (24a, 29a) and second (24b, 29b) means stopper limiting their relative rotation in two opposite directions of rotation (D, R), the torque input member (7a, 7b) and the phasing member (25) having three ε (15a, 30) and fourth (15b, 30) stop means limiting their relative rotation in two opposite directions of rotation (D, R), characterized in that the third and fourth stop means comprise at least one stop block (30) formed on the phasing member (25) or respectively on the torque input member (7a, 7b), and at least one elongated arcuate housing (15) formed on the torque input element (7a, 7b) or respectively on the phasing member (25), the stop stud (30) being inserted into the housing (15) and being able to bear against each of the ends (15a, 15b) of said housing (15), the first, second, third, fourth stop means and the housing being arranged such that the input member and the output member are adapted to be in contact with the phasing washer in an extreme position.

2. Device according to claim 1, characterized in that the elastic members (10a, 10b) are helical compression springs, said stop means being designed to limit the compressing the springs (10a, 10b) and preventing the turns of the springs from being joined during their compression.

3. Device according to claim 1 or 2, characterized in that the resilient members (10a, 10b) of the or each group are supported, on the one hand, on an annular web (21) forming the torque output member , or respectively the torque input element and, on the other hand, on two guide washers (7a, 7b) which extend radially on either side of the annular web (21) and which are movable in rotation with respect to the latter, the guide washers (7a, 7b) forming the torque input element, or respectively the torque output element.

4. Device according to one of claims 1 to 3, characterized in that the phasing member (25) comprises a radially outer annular portion (26), from which lugs (27) extend radially towards the l interior and serving to support the elastic members (10a, 10b).

5. Device according to claim 4, characterized in that the abutment stud (30) extends axially from the radially outer annular portion (26) of the phasing member (25), facing one of said tabs ( 27) of the phasing member (25).

6. Device according to one of claims 1 to 5, characterized in that the annular web (21) comprises a radially inner annular portion (22) from which support lugs (23) of the elastic members (10a, 10b) extend radially outwards and serve to support the elastic members (10a, 10b).

7. Device according to claims 4 and 6, characterized in that stop means (24a, 24b, 29a, 29b) extend circumferentially on either side of each of the tabs (23, 27) of the annular web ( 21) and the phasing member (25), so that the stop means (24a, 24b) of the annular web (21) are able to bear on the stop means (29a, 29b) of the phasing member (25).

8. Device according to claims 4 to 6, characterized in that, in a given position, abutment means (24a, 24b, 29a, 29b) extend circumferentially on either side of each of the tabs (23, 27) of the annular web (21) and of the phasing member (25), so that the stop means (24a, 24b) the annular web (21) are able to bear against the abutment means (29a, 29b) of the phasing member (25), the abutment stud (30) being able to also bear against one of the ends (15a, 15b) of the housing (1 5) of the torque input member (7a, 7b).

9. Device according to one of claims 1 to 8, characterized in that it comprises two guide rings (7a, 7b) fixed to one another by riveting and / or welding at their periphery radially. external.

10. Device according to claim 9, characterized in that one (7b) at least one of the guide washers (7a, 7b) comprises, at its radially outer periphery, deformable tongues (12) adapted to be folded over the other guide ring (7a) so as to ensure their attachment to one another.

1 1. Device according to one of claims 1 to 10, characterized in that said torque transmission device is a hydrodynamic torque converter.