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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
  • F16C25/06—Ball or roller bearings
• • 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
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
  • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2361/00—Apparatus or articles in engineering in general
  • F16C2361/43—Clutches, e.g. disengaging bearing
• • 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
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
  • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input 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
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
  • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
  • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two clutches
• • 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
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
  • F16D2021/0684—Mechanically actuated clutches with two clutch 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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
  • F16D2023/126—Actuation by rocker lever; Rocker levers therefor
• • 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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
  • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
  • F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks

Definitions

• the invention relates to a friction clutch device which comprises a reaction plate which is rotatably mounted via a bearing.
• the invention relates more particularly to a friction clutch device, in particular for a motor vehicle, which comprises: a reaction plate rotatably mounted around a rotary shaft by means of a bearing comprising a first ring axially connected to the shaft and a second ring connected to the reaction plate;
• At least one first pressure plate which is mounted to rotate with the reaction plate and which is slidably mounted axially with respect to the reaction plate;
• At least one first coaxial friction disc which is interposed axially between the reaction plate and the first pressure plate; at least one first actuating rear axial annular diaphragm which comprises flexible resilient fingers between an extreme front clutch position in which the first diaphragm axially solicites the first pressure plate for clamping the first friction disk against the reaction plate; , and an extreme rear declutching position towards which the fingers are eiastically recalled.
• This type of clutch device equips, for example, motor vehicles with a robotised gearbox in which the clutch device is actuated by an electronic control unit.
• clutch devices of this type which comprise two driven shafts.
• the clutch device then comprises two coupling means temporary, each of which is intended to temporarily couple one of the driven shafts associated with the motor shaft.
• the clutch device comprises a reaction plate, two friction discs which are arranged on either side of the reaction plate which can be alternately clamped against the reaction plate by a first and a second plate pressure. Each pressure plate can be actuated by an associated diaphragm.
• the fingers of the diaphragms are in a state of rest, that is to say that they are no longer energized, when they occupy their extreme rear declutching position.
• the invention provides a friction clutch device of the type described above, characterized in that, when his fingers are in the rearmost position, the first diaphragm acts on the reaction plate and his fingers are supported on a non-deformable mechanical element and fixed axially rearwardly with respect to the first ring of the bearing to keep the fingers of the first diaphragm energized in their extreme rear position so that the first diaphragm exerts a first axial forward preload force on the bearing through the reaction plate.
• the constant axial preload of the bearing makes it possible to limit its degradation.
• This axial precharge force also makes it possible to limit the oscillation movements of the reaction plate.
• the clutch device comprises a first actuating stop of the first diaphragm which is slidably mounted axially between an extreme forward clutch position in which eile solicits the fingers of the first diaphragm in their extreme position before clutch and an extreme position declutching rear in which the fingers of the first diaphragm are supported on the first actuating stop, the fingers of the first diaphragm thus being retained in their extreme rear declutching position against their elastic return force;
• the first actuating stop is carried by an axial sleeve which is mounted to slide axially on a guide, the sleeve being capable of abutting against a first fixed radial face stop to limit the rearward stroke of the first actuating stop to its extreme rear position;
• the first actuating stop is controlled in displacement by a first axial actuating rod, the axial displacement of the first axial actuating rod being limited in one direction by a fixed stop face so as to limit the displacement towards the rear of the first actuating stop to its rearmost position so that the fingers of the first diaphragm are kept under tension in their rearmost position;
• the displacements of the first actuating stop are controlled by means of a first fork forming a lever which is pivotally mounted about a transverse axis, the pivoting of the first fork being limited in one direction by a first fixed stop face so as to limit the rearward displacement of the actuating stop until at its extreme rear position;
• the first pressure plate is interposed between the reaction plate and the first diaphragm
• the clutch device comprises a first radially outer rear annular cover which is carried by the reaction plate, the first diaphragm being fixed on the first lid; the first axial precharge force being applied to the reaction plate via the first rear cover;
• the clutch device comprises at least a second pressure plate which is mounted to rotate with the reaction plate and which is slidably mounted axially relative to the reaction plate; at least one second coaxial friction disc which is interposed axially between the reaction plate and the second pressure plate; and at least one second rear actuating coaxial annular diaphragm which has flexible resilient fingers between an extreme front clutch position in which the second diaphragm axially urges the first pressure plate to clamp the second friction disc against the reaction plate , and an extreme rear declutching position towards which the fingers are biased resiliently;
• the clutch device comprises a second stop for actuating the second diaphragm which is slidably mounted axially between an extreme forward clutch position in which it biases the fingers of the second diaphragm in their extreme forward clutch position and an extreme position; declutching rear in which the fingers of the second diaphragm are supported on the second actuating stop, the fingers of the second diaphragm thus being retained in their extreme rear declutching position against their elastic return force;
• the second actuating abutment is carried by an axial sleeve which is mounted to slide axially on a guide, the sleeve being capable of abutting against a first radial fixed face of arrest in order to limit backward the stroke of second actuating stop to its rearmost position;
• the second actuating stop is controlled in displacement by a second axial actuating rod, the axial displacement of the second axial actuating rod being limited in one direction by a fixed stop face so as to limit the displacement towards the rear of the second actuating stop to its rearmost position so that the fingers of the second diaphragm are kept under tension in their rearmost position;
• the movements of the second actuating stop are controlled by means of a second lever fork which is pivotally mounted about a transverse axis, the pivoting of the second fork being limited in one direction by a second fixed face stopping so as to limit the rearward movement of the second actuating stop to its rearmost position;
• the second diaphragm is arranged behind the first diaphragm, the second diaphragm being capable of being annular support on the first rear cover so as to exert the axial preload force;
• the axial precharge force applied by the first diaphragm and / or the second diaphragm is at least equal to 400 N.
• FIG. 1 is an axial half-sectional view of a device of FIG. friction clutch made according to a first embodiment of the invention, wherein the fingers of the two diaphragms are in an extreme rear declutching position;
• FIG. 2 is a view similar to that of FIG. 1 in which the fingers of the first diaphragm are in an extreme forward clutch position while the fingers of the second diaphragm are in their rearmost disengaging position;
• FIG. 3 is a view similar to that of FIG.
• FIG. 1 in which the fingers of the first diaphragm are in their extreme rear declutching position while the fingers of the second diaphragm are in their extreme forward clutch position;
• FIG. 4 is a front view which shows the actuating means of the diaphragms;
• FIG. 5 is a sectional view along the sectional plane 5-5 of Figure 4 which shows the actuating means of the first diaphragm;
• FIG. 6 is a sectional view along the plane of section
• Figure 7 is a view similar to that of Figure 1 which shows the clutch device made according to a second embodiment of the invention.
• FIG. 1 diagrammatically shows a portion of a friction clutch device 10, in particular for a motor vehicle, which is produced in accordance with the teachings of the invention.
• FIG. 1 shows a clutch device 10 which is intended to temporarily couple a drive shaft 12 which is arranged axially forward and of which a rear end is shown on the left in FIG. 1, with at least one shaft led 14.
• the drive shaft 12 is rotatable about an axis of rotation "B" and is rotated by a motor (not shown) of the motor vehicle.
• the clutch device 10 shown in FIG. 1 comprises two concentric driven shafts 14A, 14B which are rotatably mounted coaxially with the drive shaft 12.
• the first driven shaft 14A forms an axial tube inside which the second shaft is arranged. led 14B.
• An end portion before free 16 of the second driven shaft 14B protrudes axially from the front end of the first tubular driven shaft 14A.
• Each of the driven shafts 14A, 14B is rotatable independently of the other.
• the driven shafts 14A, 14B are connected to a rear gearbox of which only a front end radial transverse wall 18 is shown on the right in FIG. 1.
• the front face 20 of the wall 18 of FIG. the gearbox will serve as a fixed reference point, so it will be called reference face 20.
• first driven shaft 14A corresponds to certain gear ratios of the gearbox, for example the even gear ratios
• second driven shaft 14B corresponds to other gear ratios, for example the odd gear ratios.
• the clutch device 10 comprises first temporary coupling means of the first driven shaft 14A with the drive shaft 12.
• the clutch device 10 comprises a circular radial reaction plate 22 which is rotatably mounted about the axis of rotation "B", via a bearing, constituted in the present example by a Ball bearing 24,
• the ball bearing 24 is here interposed radially between the inner cylindrical face 26 of a central orifice of the reaction plate 22 and a front end portion 28 of the first tubular driven shaft 14A.
• the inner cylindrical face 26 of the reaction plate 22 has a radial rear end shoulder face 30 against which an outer ring 36 of the ball bearing 24 is intended to be axially supported.
• the front end portion 28 of the first driven shaft 14A also has a radial end face 34 of the rear end against which an inner ring 32 of the bearing.
• ball 24 is intended to be supported axially rearwardly.
• An elastic ring 38 of the "circlip" type is also arranged in a groove of the first driven shaft 14A axially in front of the ball bearing 24.
• the inner ring 32 of the ball bearing 24 is axially locked in both directions.
• the clutch device To prevent the reaction plate 22 from rotating with an oscillating movement, the clutch device
• reaction plate 22 is thus substantially fixed axially with respect to the reference face 20 of the gearbox.
• the reaction plate 22 is rotatably connected to the drive shaft 12.
• the clutch device 10 comprises a flexible circular radiai disk 40 which is arranged at a front end of the clutch device 10 and which is attached coaxially to the drive shaft 12.
• a radially outer front cover 42 is fixed on a rear face of the flexible disk 40 by means of a screw.
• the front cover 42 is mechanically connected in rotation to a peripheral portion of the reaction plate 22.
• the flexible disk 40 comprises at its periphery a start ring 44.
• the clutch device 10 also comprises a first annular pressure plate 46 which is mounted to rotate with the reaction plate 22 about the axis of rotation "B".
• the first pressure plate 46 is more particularly arranged axially vis-à-vis a rear face 48 of the reaction plate 22.
• the first pressure plate 46 is slidably mounted axially with respect to the reaction plate 22.
• the first pressure plate 46 is mounted to slide axially on axial columns 50 which are fixed to the periphery of the reaction plate 22.
• the clutch device 10 also comprises a first coaxial friction disk 52 which is interposed axially between the reaction plate 22 and the first pressure plate 46.
• the first friction disk 52 has on both sides an annular friction lining 54 which is arranged axially vis-à-vis the first pressure plate 46.
• the first friction disk 52 is intended to be clamped against the rear face 48 of the reaction plate 22 by the first pressure plate 46 to temporarily couple the first driven shaft 14A with the drive shaft 12.
• the first disk friction device 52 is rotatably mounted to the first driven shaft 14A, and is axially slidably mounted on the first tubular driven shaft 14A between a front position clamped against the rear face 48 of the reaction plate 22 and a free rear position to which it is resiliently biased and in which the first friction disk 52 is moved away from the rear face 48 of the reaction plate 22.
• the axial clearance existing between the first friction disk 52 in its free rear position and the rear face 48 of the reaction plate 22 is very weak and, by convention, it has not been shown in Figure 1.
• the clutch device 10 also comprises a first rear axial coaxial diaphragm 56 for actuating the first pressure plate 46.
• the first diaphragm 56 comprises a radially outer ring 58 and elastic fingers 60 extending radially towards the outside. Rotational axis "B" from the ring 58 to a free inner end 62. All the fingers 60 are here identical. More particularly, the first pressure plate 46 is interposed between the reaction plate 22 and the first diaphragm 56.
• the first diaphragm 56 is supported on a first radially outer rear annular cover 64 which is fixed to the reaction plate 22.
• the first rear cover 64 is thus fixed axially with respect to the reference face 20.
• the first rear cover 64 more particularly comprises an annular radially rear bottom 66 and a cylindrical axial skirt 68 which extends forward from the periphery of the bottom 66 to the peripheral portion of the reaction plate 22 by surrounding the first plate
• the annular bottom 66 also has an axially projecting rib which is formed by an annular fold which is coaxial with the axis of rotation "B" and which extends axially rearwardly so as to present a ridge. 70 annular protruding rearward.
• the ring 58 of the first diaphragm 56 is fixed on a front face of the bottom 66 of the first rear cover 64.
• the attachment is here made by an annular flange 72 which has tabs which extend radially inwards.
• the flange 72 is attached to the first rear cover 64 by rivets so that the ring 58 of the first diaphragm 56 is axially clamped against the bottom 66 of the first rear cover 64 by the radial tabs of the flange 72.
• Intermediate portion each finger 60 of the first diaphragm 56 is axially supported on an annular portion 74 of the first pressure plate 46.
• the fingers 60 of the first diaphragm 56 thus function in the manner of a lever which is supported by its upper end against the first fixed rear cover 64.
• the fingers 60 of the first diaphragm 56 are resiliently flexible between an extreme forward clutching position of the free end 62 of the fingers 60 which is shown in FIG. and wherein the first diaphragm 56 axially urges the first pressure plate 46 to clamp the first friction disk 52 against the reaction plate 22, and an extreme rear position for disengaging the free end 62 of the fingers 60 to which the fingers 60 are resiliently biased and wherein the first pressure plate 46 is no longer biased axially so that the first friction disk is in its free rear position, as shown in Figure 1.
• the first driven shaft 14A is temporarily coupled to the drive shaft 12, and in the rearmost disengaging position, the first friction disk is spaced from the reaction plate 22 and the first pressure plate 46 so that the first shaft 14A is decoupled from the drive shaft 12.
• the first diaphragm 56 is for example made of a steel having suitable elastic properties ed.
• the clutch device 10 also comprises second temporary coupling means of the second driven shaft 14B with the drive shaft 12.
• the second coupling means thus comprise a second pressure plate 76 and a second friction disk 78 for the temporary coupling of the second driven shaft 14B with the drive shaft 12.
• the functions of the second pressure plate 76 or the second friction disk 78 are similar to those of the first pressure plate 46, respectively of the first friction disk 52 .
• the second pressure plate 76 is axially mounted opposite the front face 80 of the reaction plate 22.
• the second pressure plate 76 is rotatably connected to the reaction plate 22 by means of a second rear cover 82 which has a rear radial annular bottom 84 and a cylindrical axial skirt 86 which extends forward to the rear. at the second pressure plate 76 surrounding first fixed rear cover 64. More particularly, the second rear cover 82 is fixed to the periphery of the second pressure plate 76 by means of screws.
• the second pressure plate 76 is slidably mounted axially relative to the reaction plate 22. More particularly, the second rear cover 82 forms a slide which slides axially.
• the second sliding rear cover 82 is thus integral with the second pressure plate 76 in rotation and in axial sliding.
• the second coaxial friction disk 78 is interposed axially between the reaction plate 22 and the second pressure plate 76. It also comprises on its two faces an annular friction lining 88 which is interposed axially between the front face 80 of the reaction plate. 22 and the second pressure plate 76.
• the second friction disc 78 is intended to be clamped against the front face 80 of the reaction plate 22 by the second pressure plate 76 to temporarily couple the second driven shaft 14B with the drive shaft 12.
• the second disk friction device 78 is rotatably mounted to the second driven shaft 14B 1 and is axially slidably mounted on the front end portion 16 of the second driven shaft 14B between a rear position clamped against the front face 80 of the reaction plate 22 and a free forward position towards which it is resiliently biased in which the second friction disc 78 is remote from the front face 80 of the reaction plate 22.
• the axial clearance existing between the first friction disc 52 in its free rear position and the rear face 48 of the reaction plate 22 is very small and, by convention, it has not been shown in FIG.
• the clutch device 10 also comprises a second annular diaphragm 90 annular coaxial rear actuation of the second pressure plate 76.
• the second diaphragm 90 has a structure similar to that of the first diaphragm 56.
• the second diaphragm 90 is arranged axially behind the first diaphragm 56, it is interposed axially between the edge 70 of the first fixed rear cover 64 and a front face of the bottom 84 of the second sliding rear cover 82. More particularly, the ring 92 of the second diaphragm 90 is arranged in axial support against a front face of the bottom 84 of the second sliding rear cover 82.
• An intermediate portion of the fingers 94 of the second diaphragm 90 bears axially backwards on the edge 70 of the first fixed rear cover 64.
• the second diaphragm 90 is held in position by rivets which are fixed to the first rear cover 64.
• the rivets are more particularly arranged between two consecutive fingers 94 of the second diaphragm 90 with axial play.
• the fingers 94 of the second diaphragm 90 thus function as a lever.
• an axial actuating force which is applied forward to the free end 100 of the fingers 94 is transmitted to the cover 64, the fingers 94 bearing on the ridge 70 of the first fixed rear cover 64, then at central plateau 22.
• the fingers 94 of the second diaphragm 90 are elastically flexible between an extreme forward clutch position which is shown in FIG. 3 and in which the second diaphragm 90 biases the second pressure plate axially rearwardly 76 to clamp the first clutch. isque de friction 52 against the reaction plate 22 via the second sliding rear cover 82, and an extreme rear declutching position to which the fingers 94 are recalled elastically and in which the second pressure plate 76 is no longer biased axially so that the second friction disc 78 is in its free forward position, as shown in Figure 1.
• the second driven shaft 14B in the extreme forward clutching position, the second driven shaft 14B is coupled to the drive shaft 12, and in the rearmost disengaging position, the second driven shaft 14B is decoupled from the drive shaft 12.
• the clutch device 10 also comprises means for independently controlling the first diaphragm 56 and the second diaphragm 90.
• control means comprise a first axial stop 96 for actuating the first diaphragm 56 which is slidably mounted axially between an extreme forward clutch position, as illustrated in FIG. 2, in FIG. which it axially urges forward the free end 62 of the fingers 60 of the first diaphragm 56 in their extreme position before clutching and an extreme rear position of disengagement, as shown in Figure 3.
• control means also comprise a second abutment 98 annu lar actuation of the second diaphragm 90 which is slidably mounted axially between an extreme front clutch position in which it axially urges forward the free end 100 of the fingers 94 of the second diaphragm 90 in their extreme forward clutch position, as shown in FIG. 3, and an extreme rear declutching position, as illustrated in FIG. 1.
• the first and second actuating stops 96, 98 are respectively fixed to a first and second sliding axial sleeve 102, 104.
• the sleeves 102, 104 are slidably mounted on an axial tubular guide 106 which is fixed by a rear end to the reference face 20 of the gearbox.
• the tubular guide 106 has a fastening collar 108 which extends radially outwardly from its rear end edge.
• first sleeve 102 is slidably mounted inside the tubular guide 106 against an inner cylindrical face of the guide 106
• second sleeve 104 is slidably mounted outside the tubular guide 106 on an outer cylindrical face of the guide 106.
• the first sleeve 102 is slidably mounted around the tubular guide 106 against the outer cylindrical face of the guide 106.
• the second sleeve 104 is mounted around the first sleeve 102 so that the second sleeve 104 is axially slidable against the outer cylindrical surface of the first.
• Sleeve 102 The first sleeve 102 is thus interposed radially between the guide 106 and the second sleeve 104.
• Each stopper 96, 98 can be slidably controlled through a fork 1 10, 1 12 associated with generally radial lever forming which is pivotally mounted on a pivot 1 14 axia! around a transverse axis "C", "D".
• the pivot 1 14 associated with each fork 1 10, 1 12 extends axially projecting forwardly from the reference face 20.
• Each fork 1 10, 1 12 thus has an inner end 1 16 axial support on the sleeve 102, 104 of the abutment 96, 98 of associated actuation, and an outer end 1 18 which is connectable to an actuating rod (not shown) of axis "E" parallel to the axis of rotation "B".
• the inner ends 1 16 and outer 1 18 are arranged on either side of the pivot axis "C", “D” associated.
• an associated transmission chain which comprises the associated actuating rod of an actuator, the associated fork 1 10, 1 12 and the associated abutment 96, 98 carried by its sleeve 102, 104.
• the fingers 62, 94 of the diaphragms 56, 90 are alternately in their extreme position before clutching. In the extreme forward clutching position of its fingers 62, 94, the diaphragm 56, 90 pushes the reaction plate 22 axially forward, thereby producing the axial preload force of the ball bearing 24.
• the fingers 62, 94 of the diaphragms 56, 90 are likely to be simultaneously in their extreme rear declutching position while the reaction plate 22 rotates.
• the ball bearing 24 is no longer preloaded, may deteriorate rapidly.
• the diaphragms 56, 90 when its fingers 62, 94 are in the rearmost position, at least one of the diaphragms 56, 90 acts on the reaction plate 22 and its fingers 60, 94 are directly in contact with an element mechanical 96, 98 not deformable and fixed axially towards the rear relative to the first ring 32 of the ball bearing 24 to keep the fingers 62, 94 of said diaphragm 56, 90 under tension in their extreme rear position. Said diaphragm 56, 90 thus exerts an axial forward preload force on the ball bearing 24 via the reaction plate 22 so that the contact between the rings 32, 36 and the balls is without axial play.
• the two diaphragms 56, 90 jointly exert forward a first and a second axial preload force.
• the intensity of the axial preload force exerted by the diaphragms 56, 90 is proportional to the deflection of the fingers 60 relative to their unstressed position.
• the clutch device 10 comprises a first and a second stop face 20, 108 which are fixed relative to the reaction plate 22 which are intended to block the axial displacement towards the rear of the stops 96, 98 of actuation in their extreme rear position.
• the actuating stops 96, 98 thus form the mechanical elements which are not deformable axially and axially fixed towards the rear.
• Each stationary stop face is arranged in the chain of transmission of the diaphragm 56, 90 associated so as to retain the fingers 60, 94 of the diaphragm 56, 90 associated in their extreme rear position against their elastic return force.
• the fingers 60, 94 of said diaphragm 56, 90 are thus kept under tension in their rearmost position so that each first and second diaphragm 56, 90 exerts a first and a second axial preload force constantly associated forwards on the bearing. ball 24 through the reaction plate 22, especially when the fingers 60, 94 are in their extreme rear position.
• the first and second axial preload forces are thus only produced by the elastic deformation of the fingers 56, 94 of the first and second diaphragms 56, 90.
• axial preloading force By axial preloading force, it will be understood that the intensity of the axial preload force, or the sum of the first and second axial preload forces, is greater than a minimum intensity beyond which the balls are not may be damaged by matting, this intensity being a function of the plain bearing or the bearing used.
• the intensity of the axial preload force formed by the sum of the first and second axial preload forces of the The ispositif produced according to the teachings of the invention is at least 400 N.
• the intensity of the axial preload force may also be higher depending on the dimensions of the clutch device.
• the axial preload force may, without limitation, be equal to 1600 N.
• the clutch device 10 comprises a first face fixed stop to stop the sliding back of the first actuating stop 96 in its rearmost position in order to constantly keep the fingers 60 of the first diaphragm 56 under tension so that the first axial preload force s' constantly exerts on the ball bearing 24.
• the clutch device 10 also has a second stationary stop face for stopping the second actuating stop 98 in its rearmost position in order to constantly keep the fingers 94 of the second diaphragm 90 under tension so that the second preload force axial is constantly exerted on the ball bearing 24.
• the axial preload force is then transmitted to the reaction plate 22 which itself transmits the axial preload force to the outer ring 36 of the ball bearing 24 via its shoulder face 30.
• the rear end edge 120 of the axial sleeve 102 which carries the first stop 96 is capable of abutting against a first radial stop face to limit the rearward stroke. from the first actuating stop 96 to its rearmost position.
• the first stationary fixed radial face is here formed by the fixed reference face 20 of the gearbox.
• the rear end 122 of the sleeve 104 of the second stop 98 is also capable of abutting against a second fixed radial stop face which is here formed by the fixed front face of the collar 108 to limit towards the rear stroke of the second actuating stop 98 to its extreme rear position.
• the second actuating stop 98 holds the fingers 94 of the second diaphragm 90 in their rearmost release position under tension against the restoring force of the fingers 94.
• the fingers 94 are supported by their free end 100 against the second actuating stop 98 which is stopped in its extreme rear position by the fixed front face of the collar 108.
• the actuating rod bears axially rearward against the outer end 1 18 of the first fork 1 10 (not shown in Figure 2).
• the first fork 1 10 pivots in a clockwise direction about its transverse axis "D" so that its inner end 1 16 axially urges forward the first stop 96 of actuation.
• the latter biases the free end 62 of the fingers 60 of the first diaphragm 56 towards their extreme forward clutch position.
• the fingers 60 press axially forwards on the first pressure plate 46 while being supported on the first fixed rear cover 64.
• the first pressure plate 46 thus slides axially toward the reaction plate 22 so as to clamp the first disk friction 52.
• the first diaphragm 56 exerts the first forward axial preload force via the first pressure plate 46, and the second diaphragm 90 still exerts the second axial preload force through the first fixed rear cover 64 by being supported by the free end 100 of its fingers 94 against the actuating stop 98 in its extreme rear position.
• the fingers 60 of the first diaphragm 56 are controlled in their rearmost disengaging position as shown in Figure 1.
• the actuating rod then slides forward so as to enable the first fork 1 to be pivoted in a counter-clockwise direction.
• the fingers 60 of the first diaphragm 56 bear axially on the first stop 96 so that it moves to its rearmost disengaging position by pushing the inner end 1 16 of the first fork 1 10 which pivots in a counter-clockwise direction.
• the fingers 94 of the second diaphragm 90 are controlled to their extreme position before clutching, as illustrated in FIG. 3, the actuating rod bears axially rearwardly against the outer end 1 1 18 of the second fork 1 12.
• the second fork 1 12 pivots about its transverse axis "C" so that its inner end 1 16 biases axially forwardly second actuating stop 98. The latter axially urges forward the free end 100 of the fingers 94 of the second diaphragm 90 to their extreme position before clutch.
• the fingers 94 of the second diaphragm 90 are supported axially forward by their intermediate portion on the edge 70 of the first fixed rear cover 64.
• the ring 92 of the second diaphragm 90 exerts then axially urges towards the rearward the second sliding rear cover 82.
• the second pressure plate 76 thus slides axially towards the reaction plate 22 so as to clamp the second friction disk 78.
• the second diaphragm 90 exerts the second axial preload force forwardly via the first fixed rear cover 64, and the first diaphragm 56 always exerts the first axial preload force through the first fixed rear cover 64 by being supported by the free end 62 of its fingers 60 against the first stop 96 in its extreme rear position.
• the pivoting of the second fork 1 12 is limited in a counterclockwise direction by a radial stop face which is here formed by the reference face 20 of the gearbox so as to limit the movements of the second stop 87 of actionnism to its extreme rear position.
• the pivoting of the first fork 1 10 may also be limited by the reference face 20 so as to limit the movements of the first stop 96 of actuation, and thus the fingers 60 of the first diaphragm 56 , to their extreme rear position.
• a first axial operating rod controls the first stop, either directly or via a fork.
• the movements of the first axial actuating rod are then limited forwardly so as to limit the displacement of the first stop or the pivoting of the first fork in a counterclockwise direction by looking at FIG. 1 when the stop is controlled. in its extreme rear declutching position.
• the rearward movement of the first actuating stop is thus limited to its rearmost position.
• This third embodiment is also applicable to the second fork 1 12.
• the friction discs 52 may be replaced by an axial stack of several friction discs that are immersed or not in the oil, of the type commonly used in motorcycles.
• the clutch device 10 has only one driven shaft 14.
• the clutch device 10 then comprises only the first temporary coupling means, that is to say say a single pressure plate 46, a single friction disc 52 and a single actuating diaphragm 56.
• the clutch device 10 has no second pressure plate 76 or second friction disc 78, or second diaphragm 90 actuation.

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

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• 2007
  • 2007-09-19 FR FR0757684A patent/FR2915253B1/fr active Active
• 2008
  • 2008-04-04 KR KR1020097021610A patent/KR101501788B1/ko active IP Right Grant
  • 2008-04-04 CN CN200880018162.0A patent/CN102084148B/zh active Active
  • 2008-04-04 WO PCT/FR2008/050603 patent/WO2009037403A1/fr active Application Filing

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