Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
  • F16F15/1292—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F1/00—Springs
  • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
  • F16F1/32—Belleville-type springs
  • F16F1/324—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs

Definitions

• the invention relates to the field of torque transmission in motorized devices and relates to clutches. It relates more particularly to a clutch disc.
• Motor vehicles may be provided with a clutch disposed between the engine and the transmission.
• This clutch typically comprises a clutch mechanism and a clutch disc which has a peripheral torque transmission member and a central torque transmission member.
• the clutch When the clutch is in the engaged mode, the engine is connected to the transmission by the clutch disk.
• the peripheral torque transmission member is then generally gripped by the clutch mechanism so as to be driven by the rotation of the motor, and the central torque transmission member is rotationally integral with an element of the transmission, such as the gearbox of a vehicle.
• the clutch is controlled to its disengaged position, the clutch mechanism releases the clutch disk and the engine is decoupled from the transmission.
• the clutch disk In addition to its function of coupling the motor and the transmission, the clutch disk generally performs additional functions related to filtering motor acyclisms and other torsional oscillations.
• This filtering is typically carried out by one or more torsion dampers which are spring-damping assemblies working in torsion and allowing, during the transmission of the torque, a relative rotational movement of the peripheral member for transmitting torque with respect to the central organ of transmission of torque, and a damping of these acyclisms.
• the relative rotation may be permitted by springs and the damping may be achieved by a friction device provided with friction washers loaded axially by spring washers, so as to dissipate by friction the energy accumulated in the springs.
• the document FR2890713 describes a clutch disk including a torsion damper comprises elastic washers axial compression intended to solicit complementary friction surfaces, these spring washers comprising an annular mobile axial bearing portion extended radially by radial tabs of fixed axial support.
• the radial tabs of two consecutive elastic washers are interposed with each other and each radial tab requires a stop in rotation.
• the object of the invention is to improve the clutch disks of the prior art.
• the invention is directed to a clutch disc for connecting an engine and a transmission, comprising a peripheral member for transmitting torque and a central member for transmitting torque rotatably mounted one to the other. relative to the other along an axis, and at least one torsion damping device interposed between the peripheral torque transmission member and the central torque transmission member, the torsion damping device comprising at least one spring arranged to deform when the peripheral torque transmitting member and the central torque transmitting member rotate relative to each other, an elastic spring washer and a friction washer coaxial with the central member torque transmission and integral in rotation with a first rotating element, the elastic load washer applying an axial load on the friction washer which is arranged against a second rotating member, relative rotation being allowed between said first rotating member and said second rotating member.
• the spring load washer has an annular contact portion and at least two support legs which extend from the annular contact portion, the elastic load washer supported by its support legs on said first rotating element, and resting by its annular contact portion directly or indirectly on the friction washer.
• the elastic spring washer has at least one passage opening formed in at least one of its legs. support, the friction washer having at least one coupling tongue passing through said at least one through hole.
• the elastic spring washer and the friction washer can thus be mounted integral in rotation with the first rotating element compactly both radially and axially.
• Compactness is a goal still sought in the arrangement of the many washers constituting a clutch disk and the invention allows this compactness in a simple manner and without harming the rigidity of the various washers.
• the implementation of a wide support leg in which a closed orifice is made increases the stiffness of an elastic spring washer, in comparison with an elastic spring washer in which the wide support leg breakthrough is replaced by two legs separated by a smaller width.
• the diameter of the friction washer can be reduced without impairing its function, so as to simply cooperate with the annular contact portion of the load spring washer, and its rotation locking means can be simplified in the form of one or more coupling tabs.
• the locking means in rotation of the spring washer and / or the friction washer can thus be made less bulky thanks to the coupling tongue or tabs passing through the orifices of passage.
• the clutch disc may comprise the following additional features, alone or in combination:
• said at least one passage orifice is a closed orifice.
• the elastic spring washer comprises four support lugs distributed in two substantially perpendicular directions;
• the elastic spring washer has two through holes in each support lug; -
• the friction washer has an annular friction portion and four pairs of coupling tongues extending substantially perpendicular to the plane of the annular friction portion, towards the first rotating element;
• the elastic spring washer has a rotational stop tooth on at least one support lug, the rotational stop tooth being inserted into a rotational stop orifice formed in the first rotating element; in other words, the elastic spring washer can be mounted to rotate with the first rotating element via the tooth and the stop orifice;
• the rotational stop orifice is a rotational stop groove
• the at least one coupling tongue is fitted into the at least one through hole so that the friction washer is locked in rotation with the elastic load washer in the two directions of rotation, that is, the friction washer can be integral in rotation on the spring load washer;
• the at least one coupling tongue is further inserted into at least one end orifice formed in the first rotating element, so that the first rotating element does not obstruct the axial displacement of the elastic spring washer;
• the at least one coupling tongue is fitted into the at least one end orifice so that the friction washer is locked in rotation with the first element rotating in both directions of rotation; in other words, the friction washer can be rotatably mounted on the first rotating element;
• the clutch disc comprises a web connected to one of the central torque transmission member and the peripheral torque transmission member, and two guide washers connected to the other one of the central transmission member. of torque and the peripheral member for transmitting torque and arranged on either side of the sail, as well as springs interposed between the sail and the guide washers, the first rotating element consisting of one of the guide washers or the sail;
• the clutch disc comprises a web connected to one of the central torque transmission member and the peripheral torque transmission member, and two guide washers connected to the other one of the central transmission member. torque and the peripheral member for transmitting torque and disposed on both sides of the web, as well as springs interposed between the web and the guide washers, the first rotating element consisting of a guide washers;
• the clutch disc comprises a sail connected to the central torque transmission member, and two guide washers connected to the peripheral torque transmission member and arranged on either side of the sail, as well as springs; interposed between the web and the guide washers, the first rotating element consisting of one of the guide washers;
• the supporting lugs (19) of the elastic load washer (15) have external radial ends which are arranged against one of the guide washers, circumferentially between two consecutive springs;
• the second rotating element is an element connected to the veil
• the second rotating element is a pre-damper cassette attached to the web;
• the elastic spring washer is of substantially frustoconical shape, the annular contact portion being on the side of the tip of the cone and the support lugs being on the side of the base of the cone;
• the support tabs extend radially outwardly of the elastic load washer; the at least one coupling tongue is arranged on the outer periphery of the friction washer.
• the at least one coupling tongue extends radially outwardly of the friction washer
• the friction washer is mounted to rotate with the first rotating element and the spring load washer is mounted to rotate on the friction washer so that the spring load washer is mounted integral in rotation with the first rotating element only through the friction washer.
• At least one of the coupling tongues comprises a boss co-operating with a border of a passage orifice and forming an axial retaining element axially retaining the friction washer on the elastic load washer, thus the elastic washer of load and the friction washer can form a pre-assembled subassembly;
• the boss can be obtained by means of a method of deforming the coupling tongues, for example by means of a blasting method;
• the coupling tongues may also extend in an axial direction to promote axial retention between the boss and the associated through hole.
• FIG. 4 is an exploded view showing a load elastic washer and a friction washer of the clutch of FIG. 1;
• FIG. 5 shows in perspective the web of Figure 2 associated with the washers of Figure 4;
• Figure 6 shows the assembly of Figure 5 associated with the guide ring of Figure 3;
• Figure 8 is a detail view of Figure 7;
• Figure 9 is a detail view of Figure 3; - Figure 10 is similar to Figure 9, for an alternative embodiment;
• FIG. 11 is an alternative embodiment including an axial retaining element between the spring load washer and the friction washer.
• the terms "external” and “internal” as well as the “axial” and “radial” orientations will be used to designate, according to the definitions given in the description, elements of the torsion damper.
• the axis (X) of rotation (represented in FIG. 1) determines the “axial” orientation.
• the "radial” orientation is directed orthogonally to the axis (X).
• the “circumferential” orientation is directed orthogonally to the axis (X) of rotation and orthogonal to the radial direction.
• FIG. 1 shows in perspective a clutch disc 1 for the present example, a motor vehicle. Such a clutch disk is conventionally provided on its outer periphery with a friction disc which has not been shown.
• the clutch disc 1 is intended to connect the engine and the transmission of a motor vehicle. It comprises a peripheral member for transmitting torque, constituted here by the friction disk (not shown), and a central torque transmission member, constituted in this case by a hub 3.
• the friction disk (not shown) is integral with a set rigid consisting of two side flanges called “first guide ring 4" and “second guide ring 5", this assembly being fixed by rivets 6.
• This clutch disc 1 is conventionally mounted so that the not shown friction disc, fixed on the periphery of one of the guide washers 4, 5, can be gripped by a clutch mechanism connected to the flywheel of the motor, and that the hub 3 is connected in rotation to an input shaft of the vehicle gearbox, via an internal toothing 7 of the hub 3.
• the clutch disc 1 is provided with a torsion damping device comprising a set of springs 8 interposed between the guide washers 4, 5 and a disc, called “veil 9" which is rotated with the hub 3.
• Figures 2 and 3 respectively show the web 9 and the first guide ring 4 as they would occur if the clutch plate 1 was disassembled.
• the web 9 of FIG. 2 comprises housings 10 for the springs 8. It has a radially internal contour 11 provided with teeth for its connection in rotation with the hub 3, this connection being able to be direct, by mechanical contact, or indirectly, for example by an additional torsion damper called pre-damper.
• a cassette 16 is fixed on the web 9 and may contain this possible pre-damper.
• the cassette 16 is here made of plastic and has a friction face 12 facing towards the first guide washer 4.
• the first guide washer 4 has housings 13 for the springs 8, fixing holes 2 for the rivets 6, as well as a friction washer 14 and an elastic load washer 15 superimposed so that the friction washer 14 come into contact with the friction face 12 of the cassette 16, when the clutch disc 1 is assembled.
• the resilient spring washer 15 then exerts an axial load between the friction washer 14 and the first guide washer 4 so that the friction washer 14 is urged against the friction face 12 of the cassette 16.
• the friction washer 14 and the resilient spring washer 15 are integral in rotation with the first guide ring 4.
• the inner contour 17 of the first guide ring 4 surrounds the hub 3, but the latter can rotate freely relative to the two guide rings 4, 5 .
• FIG. 4 is a perspective view of the elastic spring washer 15 surmounted by the friction washer 14.
• the resilient spring washer 15 has an annular contact portion 18 and, in the present example, four support legs 19 which extend from the annular contact portion 18.
• the annular contact portion 18 is substantially in the form of a disc intended to exert pressure on the friction washer 14.
• the four support lugs 19 are regularly distributed over the outer contour of the annular contact portion 18, in two substantially perpendicular directions.
• the elastic spring washer 15 is made of a material chosen for its elastic properties, for example a steel, and has for example a substantially frustoconical shape to be able to fulfill its function of axial spring.
• the annular contact portion 18 is on the side of the tip of the cone while the support legs 19 are on the side of the base of the cone, which implies that the support legs 19 extend radially towards the cone. outside the load spring washer 15.
• the resilient spring washer 15 is supported by its support lugs 19 on a first rotating element of the clutch disc constituted by the first guide washer 4, and is supported by its annular contact portion 18 on the friction washer 14.
• the latter relies on a second rotating element constituted by the cassette 16 attached to the web 9.
• each support lug 19 of the resilient spring washer 15 has a pair of through holes 20 and a rotational stop tooth 22 intended to cooperate with the first guide ring 4 to make the resilient spring washer 15 integral in rotation with the first guide ring 4.
• the friction washer 14, shown in FIG. 4, comprises an annular friction portion 21 having substantially a disc shape and intended to come into contact with the friction face 12 of the cassette 16.
• the friction washer 14 is here metallic, which involves a metal friction on advantageous plastic.
• the friction washer 14 further comprises four pairs of coupling tongues 23, each extending substantially perpendicular to the plane of the annular friction portion 21.
• FIG. 5 shows the web 9, the friction washer 14 and the spring washer 15 as they are inside the clutch disk 1 when mounted.
• FIG. 5 does not show the first guide washer 4 in order to show the cooperation of the friction washer 14, the elastic load washer 15 and the veil 9.
• the resilient spring washer 15 then presses the friction washer 14 against the cassette 16, relying, thanks to its support legs 19, against the first guide ring 4.
• the coupling tongues 23 of the friction washer 14 through the passage orifices 20 of the elastic load washer 15 as shown in FIG. 5.
• the friction washer 14 coupled to the spring washer 15 is shown in perspective in FIG. 7, the coupling tongues 23 passing through the through holes 20.
• FIG. 8 is a detailed view of the assembly of FIG. 7, and shows, seen from below, one of the support lugs 19 of the elastic load washer 15 traversed by the coupling tongues 23.
• the tongues of FIG. coupling 23 also pass through end orifices 24 formed in the first guide ring 4.
• FIG. 6 is identical to FIG. 5, except that the first guide ring 4 has in this case been shown and shows the tabs coupling 23 inserted into the end holes 24.
• the friction washer 14, the resilient spring washer 15, and the first guide washer 4 are integral in rotation in several variants.
• the elastic spring washer 15 is mounted to rotate with the first guide ring 4 by virtue of each rotation stop tooth 22 which is inserted into a stop groove in rotation in the first guide ring 4.
• FIG. 3 shows the four rotational stop teeth 22 inserted in the four rotational locking grooves 25.
• Each support lug 19 of the spring load washer 15 is disposed against the first guide ring 4, with their stop tooth arranged circumferentially between two consecutive springs.
• the friction washer 14 is mounted to rotate with the resilient spring washer 15 by virtue of the coupling tongues 23 which are adjusted in width in the passage orifices 20 of the elastic load washer 15.
• the through-holes 20 have a substantially rectangular contour to provide plane-to-plane contact with the slices of the coupling tongues 23 which are fitted, or even slightly tightened, in the through holes 20 in order to guarantee the rotational drive. one washer by the other in both directions of rotation.
• the end ports 24 are wider than the coupling tongues 23 so that the coupling tongues 23 can freely pass through the end holes 24 without touching the edges.
• the width here extends in the circumferential direction.
• the end holes 24 thus do not interfere with the coupling tongues 23, they do not contribute to make the two washers 14, 15 integral in rotation.
• the end openings 24 allow only the passage of the coupling tongues 23 to pass through. that the latter do not abut axially on the first guide ring 4 when the resilient spring washer 15 is pressed against the first guide ring 4.
• the coupling tongues 23 of the friction ring 14 can be advantageously shortened axially because they are coupled in rotation only to the load washer 15.
• the friction washer 14 is rotatably mounted on the first guide ring 4 by virtue of the coupling tongues 23 which are adjusted in width in the end orifices 24 of the first guide ring 4.
• the end ports 24 have a substantially rectangular contour to provide plane-to-plane contact with the wafers of the coupling tongues 23 which are fitted or even slightly tightened in these end ports 24 to ensure rotational coupling of the friction washer 23 and the first guide ring 4, in both directions of rotation.
• the passage orifices 20 are this time of greater width than the coupling tongues 23 so that the coupling tongues 23 can freely pass through the through holes 20 without touching the edges.
• the passage holes 20 thus do not interfere with the coupling tongues 23 and only serve to allow the passage of the coupling tongue 23 through the support lug 19.
• Support tabs 19 of load spring washer 15 have no rotational stop teeth 22.
• Through holes 20, as well as end ports 24, are sized in width to be fitted to the coupling tabs. 23.
• the coupling tongues 23 are thus fitted, or even slightly tightened, in the through-holes 20 and also in the end orifices 24 so that the coupling tongues 23 provide direct coupling in both directions of rotation. , the friction washer 14 and the elastic load washer 15 with the first guide ring 4.
• FIG. 11 shows an alternative embodiment of the coupling tongues 23.
• They comprise a boss 42 cooperating with a border of a passage orifice 20 and thus forming an axial retaining element axially retaining the friction washer 14 on the Elastic load washer 15.
• the boss can be obtained by means of a method of deforming the coupling tongues, for example by means of a blasting process.
• the coupling tabs extend in an axial direction to promote axial retention between the boss 42 and the associated through port.
• annular contact portion 18 may be on the side of the base of the cone that constitutes the spring washer 15 load, while its support legs 19 are on the side of the tip of the cone, which would imply that the legs of 19 in this case, the friction washer 14 could be adapted to such a resilient washer 15, having radially extending coupling tongues 23 inward and cooperating with the support lugs 19 through the passage orifices 20.
• the torque formed by the friction washer 14 and the load elastic washer 15 may be axially located elsewhere in the clutch disk, which implies that the first and second rotary elements of the clutch disk may be other elements than, respectively, the first guide ring 4 (for example, the second guide ring 5 or another element), and the cassette 16 (for example, the veil 9 or another element), it is sufficient that one relative rotation is allowed, thanks to the torsion damper, between the first and second rotating elements.
• the invention can be applied to any of the torsion dampers.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Operated Clutches (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=59811570

Family Applications (1)

Country Status (5)

Families Citing this family (1)

Citations (5)

Family Cites Families (1)

• 2017
  • 2017-06-29 FR FR1756077A patent/FR3068410B1/fr active Active
• 2018
  • 2018-06-18 WO PCT/FR2018/051448 patent/WO2019002716A1/fr active Application Filing
  • 2018-06-18 BR BR112019027326-3A patent/BR112019027326B1/pt active IP Right Grant
  • 2018-06-18 KR KR1020197038673A patent/KR20200021949A/ko unknown
  • 2018-06-18 CN CN201880044190.3A patent/CN110809678A/zh active Pending

Patent Citations (5)

Also Published As

Similar Documents

Legal Events