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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D13/00—Friction clutches
  • F16D13/58—Details
  • F16D13/583—Diaphragm-springs, e.g. Belleville
  • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate
• • 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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D2300/00—Special features for couplings or clutches
  • F16D2300/14—Clutches which are normally open, i.e. not engaged in released state

Definitions

• the invention relates to a subassembly of a clutch mechanism for a motor vehicle, to a normally open clutch mechanism comprising this subassembly and to a double-clutch mechanism comprising, in particular, such a sub-assembly. -together.
• the invention relates to an improvement of a subassembly consisting of the diaphragm and the cover for normally open clutch mechanisms for motor vehicles and, in particular, to the double-clutch mechanisms for transmission systems. with an automatic robotised gearbox and also with so-called "KO cut-off" clutch mechanisms for hybrid transmission systems.
• a conventional clutch mechanism generally comprises, on an axis of revolution, a cover in which is housed a tilting annular diaphragm between an engaged position and a disengaged position so as to move a pressure plate.
• the pressure plate urged by the diaphragm, is intended to clamp a friction disc carrying friction linings on a reaction plate coaxial with the pressure plate and the friction disc.
• the diaphragm generally has an annular shape and carries, in its central portion, fingers extending radially inwardly. This diaphragm is mounted on the lid by means of rivets ensuring its holding while allowing its elastically reversible tilting.
• the friction disk is rotatably connected to the input shaft of the gearbox while the reaction plate is integral in rotation of the lid, the diaphragm and a flywheel connected to the motor shaft.
• the two clutches are normally open which means that the passage in the engaged position and the transmission of the engine torque requires applying a force to contact the friction linings of each clutch with the flywheel via the reaction plate. , unlike clutches normally closed in which this force is applied to the clutch.
• the active position of the diaphragm thus corresponds to a coupling of the shafts of the engine and the gearbox.
• Such a double-clutch mechanism is known, in particular, of WO 2015/180778, wherein a first diaphragm is housed between an outer cover and an inner cover enclosing a second diaphragm, the two covers being offset axially.
• the first diaphragm is supported both on a first projection carried by the inner face of the outer cover and a second projection carried by the outer face of the inner cover.
• the second diaphragm is, in turn, supported on a third projection formed on the inner face of the inner cover and on a spring washer called pre-load.
• This washer is mounted between the periphery of the second diaphragm and the pressure plate of the second clutch.
• the washer is riveted to the inner cover and forms a pivot between the disengaged position and the licking point while blocking the axial translation of the second diaphragm.
• the second diaphragm bears on the third projection of the inner cover and on the support bead of the pressure plate of the second clutch so that the engine torque is transmitted to the second transmission shaft.
• the second diaphragm In the disengaged position, the second diaphragm is supported on the third projection of the cover and on the spring washer preload.
• this pre-load washer is an additional independent piece which requires a delicate assembly operation and which contributes, in addition, by its own dimensions and mass, to increase the volume and weight of the clutch mechanism. .
• the two components of these clutch mechanisms that are the cover and the diaphragm, are generally pre-assembled at the factory to form a subset which is stored and transported and delivered to the assembly sites of the builders. vehicles for integration into vehicle transmission systems.
• the invention aims to remedy these technical problems by proposing an improved subassembly comprising a diaphragm and a cover on which is formed the pivot of said diaphragm thus avoiding the pre-load washer.
• the improvement of the invention applies, in particular, to the diaphragm and the cover of the second mechanism of a double-clutch mechanism but can also integrate advantageously with simple clutch mechanisms of the normally open type.
• a subassembly of clutch mechanism normally open comprising a diaphragm housed in a cover having a side wall and a bottom whose inner face carries a projection on which said diaphragm comes in. support, characterized in that said diaphragm carries, on its outer peripheral edge, at least two bearing lugs which extend radially and whose free ends are engaged, under stress, in counter-bearing openings which are formed in the side wall of said cover.
• the stress of effort eliminates the micro movements generated by the diaphragm on the openings when the subassembly is subjected to the vibrations of the internal combustion engine.
• This stress is included, in the engaged position, between 100 and 400 N.
• the openings of the lid are each formed by an orifice in which opens the end of the support lugs of the diaphragm, said orifice ensuring the wedging under stress of said legs between two faces of which the a form a stop for the disengaged position of the diaphragm.
• the wedging orifice is delimited by a circumferential wall whose inner face forms the abutment of the support lugs of the diaphragm in the disengaged position.
• the circumferential wall may be a blade attached and fixed on the rim of the side wall of the lid.
• the insert blade can completely cover the orifice.
• the openings of the lid have a bayonet profile consisting of an open slot for the introduction of the end of the support lugs and opening laterally in an orifice ensuring the wedging under constraints of said tabs force between two faces, one of which forms a stop for the disengaged position of the diaphragm.
• the wedge orifice extends perpendicularly to said open notch.
• the wedging hole is defined by a circumferential wall whose inner face forms the abutment of the support lugs of the diaphragm in the disengaged position.
• the circumferential wall is an attached blade and fixed on the rim of the side wall of the lid.
• the insert blade may partially cover the notch of the openings of the bayonet profile cover.
• the circumferential wall is formed by deformation of a side carried by the rim of the lid.
• the diaphragm comprises an annular portion and support lugs distributed circumferentially around the annular portion, the bearing lugs extending radially from said annular portion.
• the diaphragm comprises actuating fingers, coming from the annular portion, extending radially inwards and adapted to bear against a control stop.
• the periphery of the diaphragm is provided with petals, some at least bear said support legs.
• the support legs have a tapered profile.
• a second object of the invention is a normally open clutch mechanism characterized in that it comprises a subset as defined above and a pressure plate carrying a support bead bearing on the diaphragm.
• the diaphragm comprises an annular portion arranged, at least partially, between a projection of the cover and the support bead of the pressure plate and from which said support legs extend. radially beyond said projection.
• Another object of the invention is a double-clutch mechanism comprising a first diaphragm housed between an outer cover and an inner cover enclosing a second diaphragm, the two covers being offset axially, characterized in that the inner cover and the second diaphragm consist of a subset as defined above.
• Still another object of the invention is a hybrid transmission system comprising a normally open clutch mechanism as defined above, an electric motor and a double-clutch mechanism having the characteristics defined above.
• the invention makes it possible to ensure the wedging of the diaphragm in the cover under stress and thus to achieve a stable subset, well adapted to storage and ready for easy operation of subsequent integration into a mechanical mechanism. 'clutch.
• the invention it becomes possible to overcome the pre-load spring washer which allows to lighten the clutch mechanism and reduce its size while providing a significant gain in material.
• the diaphragm is constantly subjected to an axial force. The micro-movements of the diaphragm relative to the supports of the cover are thus limited.
• the subset of the invention is applicable to any normally open clutch mechanism.
• the invention makes it possible to integrate, in a hybrid transmission system, the combination of a clutch mechanism KO clutch and a double-clutch, at least one of the mechanisms is equipped with the -all of the invention.
• FIG. 1A is a sectional view of a hybrid transmission system comprising a KO clutch clutch mechanism incorporating on the left side the subassembly of the invention in disengaged (upper part) and engaged (part lower) and, on the right side, a double-clutch mechanism that can also integrate the subset of the invention.
• FIG. 1B is an axial half-sectional view of a double-clutch mechanism for a robotized gearbox incorporating the subset of the invention.
• Figure 2 shows schematic views of a diaphragm taken from the subset of the invention in various positions.
• Figures 3A and 3B are front views of two embodiments of the diaphragm extracted from the subset of the invention.
• Figures 4A and 4B are views, respectively, of front and exploded perspective of the subset of the invention made by the assembly of the lid and the diaphragm of Figures 3A or 3B.
• FIGS. 5A and 5B are detailed views of a first variant of the subset of the invention, respectively, at the beginning and at the end of the assembly of the diaphragm in the cover.
• FIGS. 6A and 6B are detailed views of a second variant of the subset of the invention, respectively, at the beginning and at the end of the assembly of the diaphragm in the cover.
• FIGS 7A and 7B are detail views of a third variant of the subset of the invention, respectively, at the beginning and at the end of the diaphragm assembly in the lid.
• identical or similar elements are marked with identical reference signs throughout the figures.
• FIG. 1A shows a hybrid transmission system comprising an electric motor 7 connected to a reaction plate 6, a clutch clutch mechanism KO attached to the reaction plate 6, a clutch friction disk 5 and a double clutch mechanism K2 attached to the reaction plate 6.
• FIG. 1B shows a double-clutch mechanism capable of being integrated in a hybrid transmission system in which a heat engine is associated with an electric motor (as illustrated by the embodiment of FIG. 1A) and / or in a transmission system with a robotised gearbox.
• Such a dual-clutch mechanism comprises a first mechanism and a second clutch mechanism for the passage of different ratios of parities.
• the improvement provided by the invention to these double-clutch mechanisms is to remove the elastic preload washer, as shown in Figures IA, IB.
• Such a double-clutch mechanism such as the mechanism K2 ( Figure LA), is normally open.
• the mechanism K2 is engaged, in particular, with two generally coaxial transmission shafts Al, A2 (shown schematically in FIG. 1A), connected to the robotic gearbox (not shown).
• the electric motor 7 is associated with the combustion engine embodied here by a crankshaft 8.1 and a driving shaft 8.2.
• the electric motor 7 comprises a stator 7.1 coupled to a rotor 7.2 secured to the reaction plate 6.
• the friction disc 5 carries 5.1 friction linings.
• the reaction plate 6 bears on the driving shaft 8.2 via the bearing 6.1.
• the friction disc 5 transmits the torque of the engine when the clutch cutoff mechanism KO is closed.
• the clutch mechanism KO closes automatically (position engaged, half-view lower figure). IA) under the action of a control stop 9 (mechanical or hydraulic). Closing the KO clutch mechanism causes the engine to start.
• the robotized gearbox then receives, jointly, the torque coming from the internal combustion engine and that produced by the electric motor 7.
• the double-clutch mechanism then makes it possible to distribute the overall torque on one of the two transmission shafts ( A1 or A2).
• the cutoff clutch mechanism KO comprises a diaphragm 1 .1 housed in a cover 2.2 fixed on the reaction plate 6.
• the cutoff clutch mechanism KO is normally open.
• the double-clutch mechanism comprises a first diaphragm 1.1 housed between an outer cover 2.1 and an inner cover 2.2 enclosing a second diaphragm 1.2.
• the outer cover 2.1 and the inner cover 2.2 are axially offset.
• the diaphragms 1.1 and 1.2 are cylindrical components whose central portion is provided with a central orifice 1.20 and a series of radial fingers 1.22, more particularly visible in Figures 4A and 4B, on which a control stop 9 (hydraulic or mechanical) is supported.
• the central portion is extended radially outwardly by an intermediate annular portion 1.23 profile said "belleville”.
• the covers 2.1, 2.2 have a generally hollow shape and comprise an annular bottom 2a extending in a plane perpendicular to the axis of revolution X of the double clutch and an outer side wall 2b of substantially cylindrical shape extending the bottom 2a from its outer periphery.
• the bottom 2a and the side wall 2b of the diaphragm form between them an angle of between 30 ° and 90 °.
• the first diaphragm 1.1 is supported both on a first protrusion
• the second clutch mechanism comprises a second pressure plate 4 and a reaction plate 6 'between which a friction disc 5 extends.
• the hybrid transmission system incorporates a clutch engagement mechanism KO, as illustrated by FIG. Figure IA, as well as a double-clutch mechanism K2, as shown in Figure 1B.
• the reaction plate 6 'of the double-clutch mechanism (FIG. 1B) is made integral in rotation with the reaction plate 6 connected to the electric motor 7 (FIG. 1A).
• connection of the two reaction plates 6, 6 ' is provided for example by means of screws or splines (not shown).
• the plateau reaction 6 'then receives the torque from the reaction plate 6 which is generated by the electric motor 7.
• the second diaphragm 1.2 must be mounted, as the first diaphragm, between two support zones.
• Its first bearing zone here consists of a projection 3.3 formed on the inside face of the inner lid 2.2 and the second bearing zone is formed on a cord 4.1 carried by the pressure plate 4 while the third zone of support, which was previously located on the pre-load washer, is now and according to the invention, deleted.
• the inner cover 2.2 and the second diaphragm 1.2 component the second clutch mechanism. are, in turn, modified so that the third support zone of the second diaphragm 1.2 is now located on the inner cover itself while ensuring, after its mounting in the cover 2.2, a stress prestressing of the diaphragm 1.2. This stress is between 100 and 400 N
• the diaphragm 1.2 carries, on its outer peripheral edge, at least two support lugs 1.21 and, preferably, six lugs distributed circumferentially around the axis X and which extend radially in the plane of the annular part.
• the free ends of the tabs 1.21 are intended to be engaged, under stress of effort, in openings 2.21 forming against-supports which are formed in the side wall 2b of the cover 2.2, as illustrated in FIG. 2.
• Figure 2 schematically illustrates the kinematics of the second diaphragm 1.2 and its cooperation with the cover 2.2 according to the improvement of the invention.
• the support legs 1.21 are flat and oriented at an angle between 0 ° and 15 ° with respect to the plan of the belleville part 1.23. This configuration corresponds more particularly to the diaphragm according to the embodiment of FIG. 3B.
• the support legs could have a curvilinear profile.
• the diaphragm 1.2 In the storage position illustrated by the position 2 of Figure 2, the diaphragm 1.2 is placed inside the cover 2.2 and the support lugs 1.21 are then introduced into the openings 2.21. In this position, the belleville portion 1.23 of the diaphragm 1.2 is in contact with the projection 3.3 of the cover 2.2. The diaphragm is then subjected to stress prestressing which causes pivoting of the belleville part 1.23 (shown by the arrow in FIG. 2) around an axis passing through the projection 3.3 of the cover 2.2. This preload aims to immobilize the diaphragm in the cover before subsequent assembly of the subset in a transmission system, for example, hybrid type.
• the tabs 1.21 bear against the stop face 2.31 2.21 openings by switching from an angle b opposite to the initial angle a around a circumferential inflection line 1.2a located at their junction with the belleville part 1.23.
• the belleville part 1.23 of the diaphragm 1.2 is in contact, on the one hand, with the projection 3.3 of the cover 2.2 and, on the other hand, with the cord 4.1 of the pressure plate 4.
• the fingers 1.22 are actuated by the control stop 9 and the diaphragm 1.2 reaches an intermediate position called "kissing point" or “Licking point” illustrated by the position 3 of Figure 2 (corresponding to the contacting of the pressure plate 4 with the friction disk lining 5).
• the diaphragm 1.2 remains in permanent contact with the projection 3.3 of the cover 2.2.
• the tabs 1.21 have a tapered profile whose end is rounded, as shown in Figures 3A, 3B.
• This profile is adapted to the geometry of the openings 2.21 taking here, in the embodiments shown, the form of crenellations, to reduce contact pressures and thus limit wear.
• the crenellated openings 2.21 of the cover 2.2 have a bayonet profile consisting of an open slot 2.21a extended laterally by a blind hole 2.21b.
• Notch 2.21a opens, on the one hand, on the outside on the rim 2.2 and on the other hand, in the blind hole 2.21b, as shown in Figures 5B, 6B and 7B.
• the notch 2.21a allows the introduction of the end of the tabs 1.21 in the slot 2.21 while the orifice 2.21b ensures, after rotation of a few degrees of the diaphragm 1.2, the wedging under effort stress of the legs 1.21 between two faces 2.31, 2.32 one of which 2.31 forms a stop for the storage position and the disengaged position of the diaphragm 1.2.
• the wedging orifice 2.21b extends perpendicular to the open notch 2.21a and one of its lateral faces is beveled to facilitate the introduction and the subsequent deflection of the tabs 1.21 between the disengaged and engaged positions of the diaphragm 1.2.
• the opening 2.21b wedging is delimited and closed towards the outside, by a circumferential wall 2.3 whose face 2.31 turned towards the inside of the slot 2.21 forms the abutment in the disengaged position of the diaphragm 1.2.
• the circumferential wall 2.3 is formed directly and in one piece with the side wall 2b of the diaphragm 2.2.
• the mounting of the diaphragm 1.2 is performed by positioning the tabs 1.21 to the right of the notches 2.21a and then by moving the diaphragm axially to engage the tabs in the slots 2.21, as shown in Figure 5A, to bring them to the inside beyond the plane of the circumferential wall 2.3.
• the next step is to turn the diaphragm 1.2 by an angle between 5 ° and 20 ° while applying a slight compression to pass the legs behind the wall 2.3 inside the orifice 2.21b in contact with the inner face 2.31 which has the effect of putting the diaphragm slightly under load.
• Legs 1.21 are then locked in slots 2.21 being able to move in the blind hole 2.21b between the two faces 2.31 and 2.32 when the diaphragm 1.2 goes from the disengaged position to the engaged position. However, it is not expected that the tabs 1.21 come into contact with the face 2.32 even in the engaged position.
• the circumferential wall 2.3 is formed by deformation of a flank 2.30 which protrudes axially outwardly of the cover 2.2 before mounting the diaphragm 1.2, as shown in Figure 6A .
• the mounting of the diaphragm 1.2 is performed by positioning the tabs 1.21 to the right of the slots 2.21 and then moving axially the diaphragm to engage the tabs in the orifice 2.21b, as shown in Figure 6A, until to bring them inside the crenels beyond the edge of the lid.
• the next step is then to fold the flank 2.30 by means of a tool such as a press P to place it in the circumferential extension of the rim of the lid, as shown in Figure 6B.
• a tool such as a press P to place it in the circumferential extension of the rim of the lid, as shown in Figure 6B.
• the tabs 1.21 are then locked in the slots 2.21 being able to move in the blind hole 2.21b between the two faces 2.31 and 2.32 when the diaphragm 1.2 passes from the disengaged position at the engaged position.
• Face 2.31 acts as counter-support when the diaphragm is in the disengaged position.
• the circumferential wall 2.3 is formed as a 2.33 blade which is reported by translation and then fixed on the circumferential edge of the cover 2.2 after introduction of the legs 1.21 in the slots 2.21 as illustrated by the arrows in Figure 7B. Once the blade 2.33 fixed on the rim of the cover 2.2, its inner face forms the face 2.31 abutment in support of the legs 1.21.
• the blade 2.33 can completely cover the orifice 2.21b and the notch 2.21a. According to this variant, it is also possible to provide a relief 2C made on the edge of the cover 2.2 and intended to receive the blade 2.33 without creating extra thickness.
• the tabs 1.21 are then locked in the slots 2.21 by being able to move in the blind hole 2.21b between the two faces 2.31 and 2.32 when the diaphragm 1.2 moves from the disengaged position to the engaged position.
• the face 2.31 is also used here counter-support when the diaphragm is in the disengaged position.
• the subset of the invention is applicable to any normally open clutch mechanism and can be advantageously integrated in a hybrid transmission system, by equipping the KO cutoff mechanism and / or the double-clutch mechanism.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

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• 2017
  • 2017-11-21 FR FR1760995A patent/FR3073912B1/fr active Active
• 2018
  • 2018-11-09 CN CN201880075513.5A patent/CN111373170A/zh active Pending
  • 2018-11-09 WO PCT/FR2018/052789 patent/WO2019102096A1/fr active Application Filing

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