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
  • F16D25/00—Fluid-actuated clutches
  • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
  • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
  • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
  • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
  • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
• • 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
  • F16D25/00—Fluid-actuated clutches
  • F16D25/10—Clutch systems with a plurality of fluid-actuated 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
  • F16D25/00—Fluid-actuated clutches
  • F16D25/12—Details not specific to one of the before-mentioned types
• • 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
  • F16D2021/0661—Hydraulically actuated multiple lamellae 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
  • F16D2300/00—Special features for couplings or clutches
  • F16D2300/12—Mounting or assembling
• • 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
  • F16D2300/26—Cover or bell housings; Details or arrangements thereof

Definitions

• a triple wet clutch comprising a hub guided in rotation around a reference axis of the triple wet clutch, a permanent kinematic connection between the hub and an electric machine, a first selection clutch and a second selection clutch to connect in rotation around the reference axis of the triple clutch the hub respectively to a first driven shaft and to a second driven shaft, and a cut-off clutch to connect a heat engine to the hub.
• the cut-off clutch surrounds at least part of the first selection clutch and the first selection clutch surrounds at least part of the second selection clutch, interlocking the cut-off clutch, the first selection clutch and the second selection clutch favoring axial compactness.
• the cut-off clutch consists of a first disc holder to which is fixed a flange connecting to a heat engine, a second disc holder secured to the hub, and a stack of discs, housed in an annular volume delimited radially by the first disc holder and the second disc holder and axially by the flange, the stack of discs constituting an alternation of first discs secured in rotation to the first disc holder, and second discs secured in rotation to the second holder -discs, the stack of discs being movable axially between a closing position of the clutch in which an end disc of the stack of discs, belonging to the first discs, is supported against a support zone of the flange clutch, and a disengagement end position in which the stack of discs is not in contact with the flange and the end disc is located axially at a distance from the support zone of the flange.
• the invention aims to remedy the drawbacks of the state of the art and to propose an architecture which makes it possible, after assembly of a clutch device whose flange cannot be removed, to determine a dimensional characteristic of 'a stack of discs housed in an interior volume of the clutch device in a reference opening position of the clutch.
• a clutch device comprising a first torque input disc holder, a second torque output disc holder, the first disc holder and the second disc carrier being guided relative to each other around an axis of revolution of the clutch device, a flange fixed to the first disc carrier in a non-removable manner, a stack of discs, housed in an annular volume delimited radially by the first disc holder and the second disc holder and axially by the flange, the stack of discs constituting an alternation of first discs secured in rotation to the first disc holder, and second discs secured in rotation of the second disc holder, the stack of discs being movable in translation parallel to the axis of revolution between a closing position of the clutch in which an end disk of the stack of disks, belonging to the first disks, bears against one or more support zones of the flange, and a reference opening position of the clutch in which the stack of discs is not in contact with the flange and the
• the control lights make it possible, using a measuring instrument, to control the absolute or relative position of at least two points of the end disk, when the stack of disks is in the position of reference opening of the clutch, and in particular to control the travel of the disc stack between the closing position of the clutch and the reference opening position of the clutch, which if necessary constitutes a measurement of the stroke of a clutch actuator used to drive the disc stack into the clutch position.
• the control lights also make it possible, using one or more rods, to physically move the stack of discs from the clutch closing position to the clutch reference opening position. Where applicable, certain control lights make it possible to maintain the disc stack in the reference opening position of the clutch using a tool, while checking the position or movement of the The disc stacking is carried out by one or more other control lights.
• the support zone(s) comprise several arc-shaped zones, each of the control lights being arranged circumferentially between two contiguous zones among the arc-shaped zones.
• each of the control lights is located at a distance from the two contiguous zones. This distance, which is preferably greater than 2mm in the axial direction, makes it possible to preserve sufficient mechanical strength to the flange.
• the control lights are positioned in an annular zone located delimited by a smaller circle tangent to the support zones and by a larger circle tangent to the support zones.
• each support zone is formed at the level of a fold of material of the flange projecting axially towards the stack of disks. The fold of material, which can be obtained by stamping, gives very good mechanical strength to this area.
• the support zone is preferably flat. It can be rectified.
• each of the control ports has an oval or bean-shaped cross section.
• the flange has at least three control lights, and preferably at least six control lights.
• control lights With a number of control lights greater than three, three simultaneous measurements can be made at three points of the positioning of the end disk, which allows it to be perfectly located in space. An additional light allows the introduction of an actuating rod without hindering the measurements. With six lights, it becomes possible to insert three actuating or holding rods to press at three points distributed on the end disk, and to measure the positioning of the end disk at three other points.
• control lights are circumferentially equally distributed, this to ensure the balancing of the flange.
• the flange radially covers the second disc holder and does not transmit torque.
• the flange channels the cooling fluid towards the disc stack.
• the first disc carrier is integral with a hub, the second disc carrier being located axially between the flange and the hub, in a volume delimited by the flange, the hub and the first carrier -discs.
• the hub forms an annular hydraulic chamber in which a piston slides in translation parallel to the reference axis between a disengagement end of stroke position resting against an end of stroke stop formed on the hub, and a position bearing against the stack of discs in the closing position of the clutch, the stack of discs in the reference opening position of the clutch being supported against the piston in the end of disengagement stroke position.
• the hub includes a permanent kinematic connection interface with an electrical machine.
• This permanent kinematic connection interface can be a toothing allowing the electric machine to be positioned parallel to the reference axis, but not coaxial with it.
• the first disc carrier, the second disc carrier and the stack of discs together form a cut-off clutch, for example to selectively connect a heat engine driving the second disc carrier to the hub.
• a first selection clutch makes it possible to connect the hub in rotation around the reference axis to a first driven shaft, the cut-off clutch surrounding at least part of the first selection clutch.
• a second selection clutch makes it possible to connect the hub in rotation around the reference axis to a second driven shaft, the first selection clutch surrounding at least part of the second selection clutch, the clutch device then constituting a triple clutch.
• the device thus described is preferably a wet clutch device, in the sense that in operation, oil circulation is provided in the annular volume housing the stack of discs.
• Figure 3 illustrates in perspective an interior face of a flange of the clutch device of Figure 1.
• Figure 4 illustrates in perspective an exterior face of the flange of Figure 3.
• Figure 5 illustrates, in axial section along a section plane V of Figure 3, a detail of the clutch device of Figure 1, in the clutch closing position.
• Figure 7 illustrates, in axial section along the section plane Vil of Figure 3, a detail of the clutch device of Figure 1, in the reference opening position of the clutch.
• FIG. 1 shows a triple wet clutch 10 for a vehicle with a hybrid engine.
• This triple wet clutch 10 comprises a hub 12 guided in rotation around a reference axis 100, a permanent kinematic connection 14 between the hub 12 and an electric machine 16, a first selection clutch 18 and a second selection clutch 20 for connect the hub 12 in rotation around the reference axis 100 respectively to a first driven shaft 22 and to a second driven shaft 24, and a cut-off clutch 26 to connect a heat engine 28 to the hub 12.
• This triple wet clutch 10 is designed to be positioned coaxially with the shaft of the thermal engine 28, while the axis of rotation 200 of the shaft of the electric machine 16 is parallel to the reference axis, but distant from this, so that the size of the triple wet clutch 10 in the axial direction is not significantly impacted by the electric machine 16.
• the hub has a connection interface 141 with the permanent kinematic connection 14 to the machine electric 16.
• the connection interface 141 can for example be a gear tooth meshing with an output pinion of the electric machine, or a set of one or more grooves for a transmission belt between the electric machine 16 and the hub 12.
• the cut-off clutch 26 surrounds at least part of the first selection clutch 18 and the first selection clutch 18 surrounds at least part of the second selection clutch 20, producing an interlocking of the cut-off clutch 26, of the first selection clutch 18 and the second selection clutch 20 also favoring axial compactness.
• the first selection clutch 18 comprises an input disc carrier 30 secured to the hub 12, an output disc carrier 32 secured in rotation to the first driven shaft 22, which is a hollow shaft intended to be secured in rotation to a first input shaft of a gearbox, and a stack of discs 34, housed in an annular volume 36 delimited radially by the input disc carrier 30 and the output disc carrier 32 and axially by a annular stop 38 secured to the input disk holder 30 and by a piston 40, which slides axially in an annular chamber 42 formed in the hub 12, the annular chamber 42 being intended to be supplied with pressurized fluid by a fluid circuit passing through the hub 12, as described for example in document W02021099070A1.
• the stack of discs 34 constitutes an alternation of clutch plates secured in rotation to the input disc carrier 30 and the hub 12, and clutch discs carrying clutch linings, secured in rotation to the disc carrier output 32.
• the second selection clutch 20 comprises an input disc holder secured to the hub 12 and which is here merged with the input disc holder 30 of the first selection clutch, an output disc holder 44 secured in rotation to the second driven shaft 24 which is hollow and intended to be secured to an input shaft of the gearbox, and a stack of discs 48, housed in an annular volume 50 delimited radially by the disc carrier d 'entrance 30 and the output disc holder 44 and axially by an annular stop 52 secured to the input disc holder 30 and by a piston 54, which slides axially in an annular chamber 56 formed in the hub 12, the annular chamber 56 being intended to be supplied with pressurized fluid by the fluid circuit passing through the hub.
• the annular stop 52 of the second selection clutch 20 is here distinct from the annular stop 38 of the first selection clutch 18.
• the stack of discs 48 constitutes an alternation of clutch plates integral in rotation with the input disc carrier 30 and the hub 12, and clutch discs carrying clutch linings, integral in rotation with the output disc carrier 44.
• the cut-off clutch 26 comprises a first disc carrier 58 secured to the hub 12 and to which is fixed a flange 60, a second disc carrier 62 fixed to a section of splined shaft 63 connecting to the thermal engine 28, and a stack of discs 64, housed in an annular volume 66 delimited radially by the first disc carrier 58 and the second disc carrier 62 and axially by the flange 60 and by an axially movable piston 68.
• the piston 68 slides in an annular chamber 70 formed in the hub 12, the annular chamber being intended to be supplied with pressurized fluid by the fluid circuit passing through the hub 12.
• the first discs 641 are in this case clutch plates while the second discs 642 are clutch discs carrying clutch linings, but other configurations of the stack of discs are possible, for example a inverted configuration in which the first disks 641 would be clutch disks and the second disks 642 would be clutch plates.
• This stack of discs 64 ends at each axial end with an end disc 6411, 6412 belonging to the first discs 641, therefore integral in rotation with the first disc carrier 58, the flange 60 and the hub 12.
• the flange 60 illustrated in Figures 3 and 4 is here constituted by a stamped annular sheet, which has folds of material 71 projecting towards the annular volume 66 and towards the stack of discs 64, to form as many of support zones 72 for the end disk 6411.
• Each support zone 72 is preferably machined, this machining possibly including a grinding, on the projecting end, initially convex, of the fold of material 71.
• the zones of The support 72 are coplanar.
• the folds of material 71 constitute a succession of arcs of circles in the extension of each other, interrupted by undeformed zones 74, in which control lights 76 are formed.
• the undeformed zones 74 and the control lights 76 are equally distributed and number six in the embodiment illustrated in the figures, it being understood that this number may vary.
• the control lights 76 pass through the flange 60 parallel to the reference axis 100, and open into the annular volume 66, axially facing the end disk 6411 facing the flange 60.
• the control lights 76 are positioned in a annular zone located delimited by a smaller circle tangent to the support zones 72 and by a larger circle tangent to the support zones 72.
• the distance axial is preferably greater than 2mm.
• the flange 60 has an outer periphery 78, illustrated in Figures 5 to 7, with a flat face bearing against an annular shoulder 80 of the first disc holder and an outer annular rim surrounded by an axial end wall 82 of the first disc holder 58.
• the flange 60 is preferably welded to the first disc holder 58 at the level of the interface 84 between the outer periphery 78 and the axial end wall 82. Alternatively, fixing by shrinking, crimping or bolting is also possible. In this embodiment, the flange 60 is not intended to transmit torque, this passing entirely through the first disc carrier 58, the stack of discs 64 and the second disc carrier 62.
• the stack of discs 64 is movable axially between a closing position of the clutch, illustrated in Figures 2 and 5 to 6, in which the end disc 6411 facing the flange 60 is supported against the coplanar support zones 72 of the flange 60, and a reference opening position of the clutch, illustrated in Figures 1 and 7, in which the stack of discs 64 is pressed against the piston 68 which bears against the stop 690, so that the end disc 6411 facing the flange 60 is located axially at the most large possible distance from the support zone 72 of the flange 60.
• the closed position of the clutch is a functional position which is reached at each clutch operation, when the piston 68, pushed back by the hydraulic pressure in the chamber 70 , presses on the end disk 6412 which faces it.
• the control lights 76 allow, during the assembly of the clutch device 10, after positioning the flange 60, and the case after definitive fixing of the flange 60, to measure the reference opening position of the clutch and/or the travel covered by the stack of discs 64 between the closing position of the clutch and the reference opening position of the clutch.
• the measurement of the axial displacement Y of the end flange 6411 is interesting, because it is equal to the total stroke of the piston 68 between its end position of the disengagement stroke and the position taken by the piston 68 when the stack of discs 64 is in the clutch position. In other words, this measurement allows access to the complete useful stroke of the piston 68, taking into account the dimensional dispersions due to the manufacturing and assembly tolerances of the parts of the clutch device. It also allows a conformity check at the end of assembly of the clutch device 10.
• control lights By at least one of the control lights, and preferably by at least three control lights 76, for example positioned at 120° from each other, a distance measurement is taken between the end disk 6411 and a fixed reference frame, or a position measurement of the end disk 6411 in a fixed reference frame, for example using an optical sensor. These measurements make it possible, if necessary, to determine the positioning of a plane tangent to the end disk 6411 in space relative to the fixed frame of reference.
• the pressure is released in the annular chamber and three other control ports 76 are introduced, preferably arranged at 120° from each other, three actuating rods 90 (figure 1) which come into contact with the end disc 6411, and the end disk 6411 and the stack of disks 64 are pushed back into the reference opening position of the clutch using the three rods 90.
• the piston 68 is actuated by filling the chamber 70 with compressed air, to bring the clutch device 10 to the clutch closing position.
• Three rods 90 are placed in contact with the end disk 6411 and the position of the three rods 90 is memorized in the clutch closing position. The pressure is released in the annular chamber 70 and the stack of discs 64 is pushed back into the reference opening position of the clutch using the three rods 90.
• the movement of the three rods 90 is measured between the closing position of the clutch and the reference opening position of the clutch, which corresponds to the stroke Y of the end disk 6411.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)
• Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=85036914

Family Applications (1)

Country Status (3)

Family Cites Families (4)

• 2022
  • 2022-11-24 FR FR2212294A patent/FR3142518B1/fr active Active
• 2023
  • 2023-11-13 WO PCT/EP2023/081578 patent/WO2024110232A1/fr not_active Ceased
  • 2023-11-13 EP EP23801492.2A patent/EP4623218A1/de active Pending

Also Published As

Similar Documents

Legal Events