EP4163732A1 - Kupplungsuhrmechanismus - Google Patents

Kupplungsuhrmechanismus Download PDF

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Publication number
EP4163732A1
EP4163732A1 EP22199695.2A EP22199695A EP4163732A1 EP 4163732 A1 EP4163732 A1 EP 4163732A1 EP 22199695 A EP22199695 A EP 22199695A EP 4163732 A1 EP4163732 A1 EP 4163732A1
Authority
EP
European Patent Office
Prior art keywords
clutch
wheel
shaft
rigid
clutch disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22199695.2A
Other languages
English (en)
French (fr)
Inventor
Thibaud Faivre Chalon
Armand Kamanda
Antoine Leveque
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LVMH Swiss Manufactures SA
Original Assignee
LVMH Swiss Manufactures SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LVMH Swiss Manufactures SA filed Critical LVMH Swiss Manufactures SA
Publication of EP4163732A1 publication Critical patent/EP4163732A1/de
Pending legal-status Critical Current

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0823—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/001—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power
    • G04B11/003—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power with friction member, e.g. with spring action
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0823—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement
    • G04F7/0828—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement acting in the plane of the movement

Definitions

  • the present invention relates to a clockwork clutch mechanism.
  • the present invention also relates to a timepiece movement comprising such a mechanism, as well as a timepiece, for example a chronograph watch, in particular a wristwatch chronograph, comprising such a mechanism or such a movement.
  • a chronograph watch for example a chronograph watch, in particular a wristwatch chronograph, comprising such a mechanism or such a movement.
  • the mechanism according to the invention can be used to produce a clutch in a chronograph watch, it is not limited to such an application, but it can also be used for any other horological application which requires a clutch: for example and in a non-limiting way, it can be used in a striking clockwork mechanism.
  • a chronograph watch is a timepiece that can be used to measure time.
  • a chronograph watch comprises at least one indicator (such as a hand) which can be started and then stopped, by means of a pusher or another control member, in order to measure a duration. Then it can be returned to its starting point.
  • chronograph watches also include indicators for displaying the current time in addition to displaying the duration measured.
  • the usual chronograph watches take the energy necessary for the operation of the part of the movement allowing the measurement of a duration on the kinematic chain allowing to count and display the current time, that is to say on the kinematic chain linking an energy source, for example a barrel, to the regulating organ and to the watch wheels, which are linked to watch indicators to display the current hour, minute and/or second.
  • an energy source for example a barrel
  • Two main members are used in the majority of operations of mechanisms for chronograph watches, namely control devices and clutch devices.
  • control devices can be for example cam or column wheel. As they are known per se in the field of the art, they will not be described here.
  • the clutch devices make it possible to drive the kinematic chain of the chronograph by the kinematic chain making it possible to count and display the current time.
  • the clutch devices make it possible to start and stop the chronograph kinematic chain very quickly, and also to block it by keeping the chronograph indicators stopped.
  • Vertical clutch devices allow a so-called “vertical” clutch between the two kinematic chains, in particular between a wheel of one kinematic chain and a wheel of the other kinematic chain.
  • Lateral or horizontal clutch devices make it possible to couple two wheels by bringing them into contact by their periphery, in particular by their teeth.
  • the disadvantage of this type of clutch is that when driving the chronograph wheel it is possible to have a starting jump caused by a misalignment of the teeth of the two wheels. The gap is all the more reduced as there are teeth.
  • gears with many teeth are difficult to manufacture and more subject to wear. In this type of device, there is no oscillating movement or tilting of the elements of these devices.
  • oscillating pinion clutch devices which allow transmission of energy from one wheel of one driveline to a wheel of the other driveline using an oscillating pinion.
  • This oscillating pinion comprises a first toothing which is in permanent contact with the wheel of the kinematic chain which makes it possible to determine the current time.
  • This oscillating pinion under the action of an actuating device such as a rocker, oscillates or rocks, so that its second toothing comes into contact with the wheel which makes it possible to carry out a measurement of a duration , thus also putting it in rotation.
  • the clamps move away from the clutch disc, thus releasing the chronograph wheel.
  • the isolator drives the isolation wheel in rotation, which has the effect of radially displacing the clutch elements using the tenons. In this way, the clutch spring comes into contact with the drive plate, thus starting the chrono.
  • the clutch mechanism described is complex and comprises more than ten parts.
  • the actuation of the clutch disc is indirect and is done via tenons.
  • several contacts take place between the different components (drive plate ⁇ clutch elements ⁇ spring ⁇ disc ⁇ friction spring ⁇ ring ⁇ axis), which leads to a significant loss of energy.
  • the document EP3671370 describes another clutch mechanism, in which, when a gripper is actuated in order to start the chronograph, its support element moves away from a clutch disc. At this time, elements pivot under the effect of springs. Positioned studs then abut against a chronograph wheel, which ensures the coupling and therefore the clutch.
  • This clutch mechanism is complex, since it requires a clutch disc having elements arranged to pivot under the action of flexible blades and to accommodate tenons which are perpendicular to the plane of the disc. Since these studs perform the clutch with the chronograph wheel, the friction surface between the chronograph wheel and each of these studs is small, which reduces the reliability of the clutch.
  • the mechanism described comprises several parts (clutch disc, several tenons, etc.), which does not facilitate the assembly of the mechanism, in addition to being complicated by the mounting of the tenons in the disc.
  • An object of the present invention is to provide a clutch mechanism free from the limitations of known clutch mechanisms.
  • Another object of the invention is to provide a clutch mechanism which comprises fewer components than the known clutch mechanisms.
  • Another object of the invention is to provide a clutch mechanism that is less bulky than the known clutch mechanisms.
  • Another object of the invention is to provide a clutch mechanism which is easier to mount than the known clutch mechanisms.
  • clutch disc or second wheel integral with the shaft
  • the expression “clutch disc (or second wheel) integral with the shaft” indicates that the disc (or the second wheel) and the shaft can be driven one by the other in a movement common, without necessarily being attached (e.g. directly attached) to each other.
  • a clutch disc frictionally bonded to the shaft is also integral with the shaft.
  • the clockwork clutch mechanism is arranged to switch, under the action of the control device, from an engaged position to a disengaged position and vice versa.
  • the first wheel drives the second wheel (the drive not necessarily being direct), and in the disengaged position the first wheel no longer drives the second wheel.
  • the expression “flexible blade” designates a blade or a beam, arranged to deform elastically in the plane of the clutch disc, for example according to a bending movement.
  • rigid clutch elements designates parts of the clutch disc which are not intended to be deformed during operation of the mechanism according to the invention, and whose rigidity is greater to that of flexible blades.
  • peripheral rigid clutch elements denotes rigid clutch elements which are at the periphery of the clutch disc and in particular which define its outer diameter.
  • clutch disc diameter refers to the largest dimension of the clutch disc.
  • the first wheel Since the first wheel is arranged to be freely rotatably mounted on the shaft, its rotation in the disengaged position does not cause rotation of the shaft nor that of the second wheel. On the other hand, in the engaged position, the rotation of the first wheel allows the rotation of the shaft, and therefore of the second wheel which is integral with the shaft, via the clutch disc.
  • the clutch is produced by a single component, namely the clutch disc, without the need for tenons or a plurality of components which come into contact with each other to produce the clutch between the first wheel and the second wheel.
  • the clutch mechanism according to the invention is less bulky than the known clutch mechanisms and can be used for example in timepieces having reduced thickness.
  • the clutch mechanism is easier to mount than known clutch mechanisms.
  • the peripheral rigid clutch elements move, under the action of the flexible blades, with a movement which is a movement substantially of translation (or “quasi-translation”) in a radial direction of the clutch disc, between the engaged position and that disengaged.
  • the clutch disc contracts (in the disengaged position) and expands (in the engaged position) under the action of the flexible blades.
  • peripheral rigid clutch elements The movement of the peripheral rigid clutch elements is a substantially translational movement because there is also a slight rotation of these elements around the central hub which is due to the deformation of the flexible blades. However, this rotation, of the order of magnitude of a few degrees, in particular less than 10°, is negligible with respect to the radial translation of the peripheral rigid clutch elements.
  • the first wheel comprises a housing arranged to receive the clutch disc at least partially in the direction of the shaft.
  • each flexible blade in the engaged position, is substantially straight. This makes it possible to reduce the low rotation of the clutch disc due to the deformation of the flexible blades, when passing from the engaged position to that disengaged and vice versa.
  • the peripheral rigid clutch elements are in the shape of an arc of a circle and/or comprise a portion in the shape of an arc of a circle. In one embodiment, this circular arc has an angular opening comprised in the range between 20° and 170°, for example comprised in the range 30° to 120°. In one embodiment, the peripheral rigid clutch elements all have the same dimensions and/or the same shape. In another embodiment, they do not all necessarily have the same dimensions and/or the same shape.
  • the clutch disc comprises a pair of parallel flexible blades connecting at least one element peripheral rigid clutch to the central hub. This makes it possible to further reduce the low rotation of the clutch disc due to the deformation of the flexible blades, when passing from the engaged position to that disengaged and vice versa. In other words, the fact of having two parallel blades makes it possible to come close to guiding in translation.
  • the second wheel is a chorograph wheel and the central hub comprises central flexible blades, these central flexible blades being arranged to make it possible to adjust the value of the torque for which the shaft slips during a reset. zero.
  • the central hub is arranged to limit the deformation of the central flexible blades.
  • the central hub comprises at least two central rigid elements defining the first diameter in the engaged position, and the second diameter in the disengaged position.
  • the central rigid elements approach in the engaged position, and move away in the disengaged position and when resetting the chorograph wheel.
  • the gripper comprises a frame which does not move during passage from the engaged position to the disengaged position.
  • this clamp can be combined with another clockwork clutch mechanism according to the invention , in particular with a clockwork clutch mechanism comprising a clutch disc different from that according to the invention and/or without a clutch disc.
  • the present invention also relates to a timepiece movement comprising the timepiece clutch mechanism according to the invention.
  • the present invention also relates to a timepiece, for example a chronograph watch, comprising the mechanism according to the invention or the timepiece movement according to the invention.
  • FIG. 1A illustrates a cross-sectional view of a clutch mechanism 100 according to one embodiment of the invention, in the engaged position.
  • a first wheel 4 (or clutch housing) is crimped on a ring 7 which is mounted in a freely rotatable manner on the axis 3 between a collar 8 and the ring 7.
  • This first wheel 4 is provided with peripheral toothing 41 which is arranged so that the first wheel 4 can rotate continuously, for example by meshing with a barrel gear train (not shown).
  • a second wheel 2 which is for example a chronograph wheel, is mounted integral with the shaft 3, for example clamped to the shaft 3.
  • the second wheel 2 is driven by the shaft 3 in a common movement.
  • the second wheel is mounted on the shaft 3 on the opposite side of the first wheel 4. The second wheel 2 is not in direct contact with the clutch disc 5 nor with the first wheel 4.
  • the 100 clutch mechanism shown in the Figure 1A also comprises a clamp 1, partially visible, which comprises two branches or jaws 10 controlled by a control device (not illustrated in the Figure 1A ), for example and without limitation a column wheel (as illustrated in the figure 2 ).
  • the jaws 10 are arranged to come into direct contact with the clutch disc 5, in particular with an outer surface P of the peripheral rigid clutch elements 51.
  • the gripper 1 moves away from the clutch disc 5.
  • the clutch disc, and in particular its surface F, then comes into contact with an (internal) cylindrical surface 42 of the first wheel 4, visible on the Figure 1A .
  • the clutch disc 5 has a first diameter so that its peripheral rigid clutch elements 51, and in particular their surface F, comes into contact with the surface 42 of the first wheel 4.
  • the first wheel 4 drives through this contact the clutch disc 5, the clutch disc 5 therefore driving the shaft 3, and the shaft 3 driving the second wheel 2, by performing a radial friction clutch.
  • the coupling of the shaft 3 and therefore of the second wheel 2 is then carried out.
  • the first wheel 4 comprises a housing 40 arranged to receive at least partially in the direction A of the shaft 3 the clutch disc 5, so as to make contact between the peripheral rigid clutch elements 51 of the disc of clutch 5 and at least a portion of surface 42 axially delimiting this housing 40.
  • this housing is substantially cylindrical.
  • clamp 1 acts on surface F of clutch disc 5 which is not received in this housing 40.
  • FIG 1B illustrates a sectional view of the clutch mechanism 100 of the Figure 1A , in the disengaged position.
  • a control member for example the column wheel 9 of the figure 2
  • the clamp 1 acts on the control device (for example the column wheel 9 of the figure 2 ), and causes the clamp 1 to close.
  • a space E is then created between the surface 42 of the first wheel 4 and the clutch disc 5.
  • the clutch disc 5 therefore contracts radially (ie in a plane perpendicular to the shaft 3) thereby blocking the axis 3 and the second wheel 2, which therefore stops.
  • the first wheel 4 continues to spin freely on the shaft 3.
  • the expansion of the clutch disc in the engaged position (visible in Figure 1A ) during the separation of the clamp 1 is made possible by a slightly pre-stressed assembly of the clutch disc 5 in the first wheel 4.
  • FIG. 3A illustrates a top view of a clutch disc 5 of a clutch mechanism 100 according to one embodiment of the invention, in the engaged position
  • Figure 3B illustrates a view from above of the clutch disc 5 of the Figure 3A , in the disengaged position.
  • a flexible blade 52 can be parallelepipedal, or have another shape, so as to promote the desired mode of deformation and to block undesirable modes of deformation.
  • Non-straight flexible strips 52 for example curved flexible strips, can also be imagined.
  • the section of the flexible blades 52 is advantageously rectangular, but could also be different.
  • the clutch disc 5 comprises three peripheral rigid clutch elements 51, this number being a good compromise between the length of the peripheral rigid clutch elements 51, which must be large enough to achieve good friction with the first wheel 4 , and at the same time which must be small enough to achieve efficient closing of the clutch disc 5 in the disengaged position.
  • the number of peripheral rigid clutch elements 51 is 2N+1, N being an integer equal to or greater than 1.
  • peripheral rigid clutch elements 51 all have the same shape (in an arc of a circle) and the same dimensions.
  • the section of the peripheral rigid clutch elements 51 is advantageously rectangular, but could also be different.
  • peripheral rigid clutch elements 51 do not all necessarily have the same shape or the same dimensions.
  • each peripheral rigid clutch element 51 is connected to the central core 53 via a pair of flexible blades 52 parallel to each other. This makes it possible to further reduce the small rotation of the clutch disc 5 due to the deformation of the flexible blades 52, when passing from the engaged position to the disengaged position and vice versa.
  • the presence of this pair of flexible blades 52 is not necessary, a single flexible blade 52 connecting each peripheral rigid clutch element 51 to the central hub 53 being sufficient for the operation of the clutch mechanism 100 according to the invention.
  • the central hub 53 is substantially rigid. In another embodiment, the central hub 53 is constituted by flexible blades 52, or else also comprises flexible blades 52.
  • the flexible blades 52 connect a free end of each peripheral rigid clutch element 51 to the central hub 53.
  • the flexible blades 52 connect another portion of each peripheral rigid clutch element 51 (for example a central portion) to the central hub 53.
  • peripheral rigid clutch elements 51 define the outer diameter of the clutch disc 5.
  • a first space E1 separates a peripheral rigid clutch element 51 from the adjacent one.
  • the clutch disc In the engaged position, visible on the Figure 3A , the clutch disc has a first diameter D1. In the disengaged position, visible on the Figure 3B , the flexible blades 52 deform under the action of the clamp 1 so that the clutch disc 5 has a second diameter D2 smaller than the first diameter D1.
  • the maximum dimension D2 of the clutch disc in the disengaged position is therefore smaller than the maximum dimension D1 of the clutch disc in the engaged position.
  • the clutch disc 5 in other words contracts, and the space E2 between a peripheral rigid clutch element 51 and the adjacent one decreases (E2 ⁇ E1). In other words, the peripheral rigid clutch elements 51 come together in the disengaged position, during the contraction of the clutch disc 5.
  • the clutch disc in the disengaged position, can register in a virtual disc smaller than that in which it can register in the engaged position.
  • the peripheral rigid clutch elements 51 move, under the action of the flexible blades 52, with a movement which is substantially a movement of translation (or “quasi-translation”) in a radial direction of the clutch disc 5 , between the engaged position ( Figure 3A ) and the disengaged one ( Figure 3B ).
  • the clutch disc 5 contracts (in the disengaged position) and expands (in the engaged position) under the action of the flexible blades 52.
  • the movement of the peripheral rigid clutch elements 51 is a substantially translational movement because there is also a slight rotation around the center C of the clutch disc 5 due to the deformation of the flexible blades 52. However, this rotation, of the order of magnitude of a few degrees, in particular less than 10°, is negligible with respect to the radial translation of the peripheral rigid clutch elements 51.
  • each flexible blade 52 in the engaged position, is substantially straight or rectilinear, as for example visible on the Figure 3A .
  • FIG 4A illustrates a top view of a clutch disc 5 of a clutch mechanism 100 according to another embodiment of the invention, in the engaged position.
  • FIG 4B illustrates a perspective view of the clutch disc 5 of the figure 4A .
  • the clutch disc 5 of the figures 4A and 4B comprises in total two first peripheral rigid clutch elements 51' and two second peripheral rigid clutch elements 51", the first and the second elements 51', 51" being arranged alternately.
  • each internal rigid clutch element 54 extends from the central hub 53.
  • Each internal rigid clutch element 54 is also connected to both a first and a second peripheral rigid clutch element 51', 51" via a pair of parallel flexible blades 52, straight in the engaged position.
  • these two pairs of parallel flexible blades 52 are arranged substantially perpendicular to each other.
  • each pair of parallel flexible blades 52 is connected to the corresponding peripheral rigid clutch element 51 via an intermediate rigid clutch element 55 which is substantially perpendicular to the adjacent pair of parallel flexible blades 52.
  • the advantage of the embodiment of the figures 4A and 4B resides in the fact that the actuation of the disc 5 can be carried out on any peripheral rigid clutch element 51 of the disc 5 and at least on a single element 51, since all the elements 51 are connected to each other.
  • a gripper 1 is not necessary to actuate the clutch, because this actuation can also be achieved for example by an arm with a single point of contact with a peripheral rigid clutch element 51.
  • the radial displacement of a single element 51 causes the displacement of all the other elements 51.
  • the clutch disc 5 has, on a macroscopic scale, a behavior similar to that of auxetic materials.
  • each intermediate rigid clutch element 55 associated with a peripheral rigid clutch element 51" (on the left and on the right of the figures 4A and 4B ) is connected via a first flexible blade 56' to one end of an adjacent first peripheral rigid clutch element 51', and via a second flexible blade 56" to one end of a second peripheral rigid clutch element 51' adjacent.
  • FIG 5A illustrates a top view of a clutch disc 5 of a clutch mechanism 100 according to another embodiment of the invention, in the engaged position.
  • FIG 5B illustrates a perspective view of the clutch disc 5 of the figure 5A .
  • the central hub 53 comprises central flexible blades 530.
  • these central flexible blades 530 form a friction system in the center of the disc.
  • the level of penetration on the diameter of the shaft 3 and/or the flexibility of the three central blades 530 make it possible to adjust precisely the value of the torque for which the shaft 3 slips during the reset.
  • each central blade 530 is connected to at least one flexible blade 52 (or to a pair of parallel flexible blades in the illustrated embodiment) via an internal rigid clutch element 54 of the central hub 53.
  • the flexible blade(s) 52 is (are) also connected to the rigid peripheral clutch element 51 corresponding.
  • the central hub 53 is arranged so as to limit the deformation of the central blades 530, in particular when the clamp 1 is actuated.
  • the central hub 53 and in particular the part of the central hub 53 which is close to the central blades 530, acts as an abutment for the central blades 530.
  • peripheral rigid clutch elements 51 is three, this number is not limiting and another number of peripheral rigid clutch elements 51 equal to or greater than two can be envisaged.
  • FIG. 6A illustrates a top view of a clutch disc 5 of a clutch mechanism 100 according to another embodiment of the invention, in the engaged position.
  • FIG. 6B illustrates a perspective view of the clutch disc 5 of the Figure 6A .
  • the clutch disc 5 in the disengaged position and when resetting, has a smaller diameter than that of the engaged position, and the central hub 53 has a larger diameter than that of the engaged position. engaged.
  • the peripheral rigid clutch elements 51 move radially towards the center C of the clutch disc 5 and therefore towards the shaft 3, while its hub central 53 deviates from the shaft 3. This also makes it possible to precisely adjust the friction torque for the reset.
  • the central hub 53 comprises at least two central rigid elements 531 defining the first diameter of the central hub 53 in the engaged position, and the second diameter in the disengaged position.
  • the central rigid elements 531 come together in the engaged position (visible on the figures 6A and 6B ), and move away in the disengaged position and when resetting the chronograph wheel (not shown).
  • the central hub 53 comprises central rigid elements 531.
  • each central rigid element 531 is connected via an internal rigid clutch element 54 to two pairs of parallel flexible blades 52', 52": a first pair connects the internal rigid clutch element 54 to an adjacent internal rigid clutch element 54, and a second pair 52" connects the rigid clutch element internal 54 to a peripheral rigid clutch element 51.
  • Each pair of 52', 52" parallel blades figures 6A and 6B can be replaced by a single flexible blade.
  • peripheral rigid clutch elements 51 is three, this number is not limiting and another number of peripheral rigid clutch elements equal to or greater than two can be envisaged.
  • the overall torque of the clutch disc 5, including the torque related to friction with the first wheel 4 and the torque related to the deformation of the flexible blades 52, is included in the range of 0.04 N mm at 0.09 N mm.
  • FIG. 7 illustrates a top view of a clamp 1 of a clutch mechanism 100 according to another embodiment of the invention.
  • the rigid body 13 moves in translation in a first direction R in a plane of the gripper 1, causing a translational movement of the jaws in a second direction M1, M2 (M1 having a direction opposite to M2) in this plane, the second direction M1, M2 being substantially perpendicular to the first direction R, the two jaws 10 approaching (in the disengaged position) respectively moving away (in the engaged position) during their movement.
  • Clamp 1 may also include an outer frame 14 which does not move when changing from the engaged position to the disengaged position.
  • the frame 14 has a U-shape and defines a space receiving the jaws 10 and the rigid body 13.
  • the frame 14 comprises holes 140 of different sizes, which allow its fixing in a movement. However, the presence of these holes 140 is not necessary and any other means of fixing the clamp 1 to the movement can be used by those skilled in the art.
  • the two jaws 10 in the disengaged position therefore close concentrically on the clutch disc 5 (not shown). These jaws move in translation along a substantially rectilinear trajectory. In one embodiment, this movement is obtained by means of two mechanisms for moving the jaws 120 arranged between the frame 14 and the jaws 10.
  • each mechanism for moving the jaws 120 comprises a rigid element 17 arranged between two flexible blades 12.
  • the mechanism for moving the jaws 120, and in particular the flexible blade(s) 12, deform(s) when passing from the engaged position to the disengaged position and vice versa, allowing the guiding quasi-linear jaws 10.
  • Rocker 19 is pushed in correspondence of its head 190 by a control device, for example a column wheel 9, in the direction of arrow B of the figure 7 .
  • the first flexible blade 18 makes it possible to produce a pivot and acts as a lever, allowing a change of direction at the other end of the rocker 9 (arrow C of the figure 7 ).
  • the flexible blade 17 makes it possible to compensate for the effect of the rotation of the rocker 19.
  • the flexible blades 16 make it possible to obtain a reversal of trajectory, that is to say they make it possible to transform the movement of the rigid body 13 along the direction R into a movement of the jaws 10 along the direction M1, M2.
  • the mechanisms for moving the jaws 120 allow a quasi-linear guiding of the jaws 10.
  • FIG 8 illustrates a perspective view of the gripper 1 of the figure 7 , cooperating with a control device, for example a column wheel 9.
  • head 190 of rocker 19 is at the bottom of a column of column wheel 9.
  • clamp 1 is therefore not controlled and is open (engaged position).
  • pliers 1 are illustrated in the figures 9 to 11 .
  • clamp 1 comprises a first U-shaped rigid body 13′ connected to rocker 19 via flexible blade 17, and a second rigid body 13′′ opposite first 13′ and C-shaped.
  • the mechanisms for moving the jaws 120 in this case comprise two flexible blades, which are not necessarily parallel, one flexible blade connecting the first rigid body 13' to a jaw 10 and the other flexible blade connecting the second rigid body 13" to this jaw 10.
  • the frame comprises part 13" and the two flexible blades 23 located on either side of part 13'.
  • FIG 10 illustrates a top view of a clamp 1 of a clutch mechanism 100 according to another embodiment of the invention.
  • the clamp 1 comprises a first rigid body 13′ in the shape of a U and connected to the rocker 19 via the flexible blade 17, and a second rigid body 13′′ opposite the first 13′ and in the shape of a C.
  • a flexible blade 16 connects each of the jaws 10 to the first rigid body 13', a pair of parallel flexible blades 120 connecting each of the jaws 10 to the second rigid body 13".
  • rocker 19' cooperates with first rigid body 13' via a second rocker 19".
  • FIG 11 illustrates a top view of a clamp 1 of a clutch mechanism 100 according to another embodiment of the invention.
  • the movement mechanism of the jaws 120 connecting each jaw 10 to the rigid body 13 comprises a specific arrangement of rigid bodies and flexible blades, allowing the transformation of the movement into translation of the rigid body 13 in a first direction in the plane of the clamp 1, in a translational movement of the jaws in a second direction in this plane, the second direction being substantially perpendicular to the first direction.
  • the flexible blades and/or the rigid bodies of the clutch disc 5 or of the clamp 1 belong to the same plane, which is that of a planar plate.
  • the plate can be produced by photolithography from a wafer, for example a silicon wafer, by laser cutting, by LIGA, etc.
  • the clutch disc 5 or the clamp 1 is made of a composite material comprising a forest of juxtaposed nanotubes held by a matrix.
  • the nanotubes are carbon nanotubes.
  • the matrix comprises amorphous carbon.
  • the nanotubes are made of other materials, for example boron nitride (“boron nitride nanotubes”, BNNT) or silicon.
  • the clutch disc 5 or the clamp 1 is made of steel.
  • the clutch disc 5 or the clamp 1 is made of glass, sapphire or alumina, of diamond, in particular of synthetic diamond (in particular synthetic diamond obtained by a process of chemical vapor deposition ), titanium, titanium alloy (in particular an alloy from the Gum metal (R) family) or an alloy from the Elinvar family, in particular Elinvar (R), Nivarox (R), Thermelast ( R), NI-Span-C (R) and Precision C (R), in shape memory alloy, in particular in Nitinol, in plastic or in any other material with a Young's modulus very little sensitive to variations in temperature.
  • synthetic diamond in particular synthetic diamond obtained by a process of chemical vapor deposition
  • titanium, titanium alloy in particular an alloy from the Gum metal (R) family
  • Elinvar family in particular Elinvar (R), Nivarox (R), Thermelast ( R), NI-Span-C (R) and Precision C (R)
  • shape memory alloy in particular in Nitinol, in plastic or in any other material with a Young

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Operated Clutches (AREA)
  • Electromechanical Clocks (AREA)
EP22199695.2A 2021-10-11 2022-10-05 Kupplungsuhrmechanismus Pending EP4163732A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH070378/2021A CH719048A9 (fr) 2021-10-11 2021-10-11 Mécanisme horloger d'embrayage.

Publications (1)

Publication Number Publication Date
EP4163732A1 true EP4163732A1 (de) 2023-04-12

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Application Number Title Priority Date Filing Date
EP22199695.2A Pending EP4163732A1 (de) 2021-10-11 2022-10-05 Kupplungsuhrmechanismus

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EP (1) EP4163732A1 (de)
CH (1) CH719048A9 (de)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2085832A1 (de) 2008-02-04 2009-08-05 Frédéric Piguet S.A. Chronographenvorrichtung mit Reibungskupplung
EP2897002A2 (de) * 2014-01-16 2015-07-22 Richemont International S.A. Isolierter Schleppzeigermechanismus und mechanische Uhr, die einen Chronografenmechanismus mit einem solchen isolierten Schleppzeigermechanismus umfasst
EP3671370A1 (de) 2018-12-20 2020-06-24 Patek Philippe SA Genève Kupplungsvorrichtung und chronographenmechanismus, der eine solche kupplungsvorrichtung umfasst

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2085832A1 (de) 2008-02-04 2009-08-05 Frédéric Piguet S.A. Chronographenvorrichtung mit Reibungskupplung
EP2897002A2 (de) * 2014-01-16 2015-07-22 Richemont International S.A. Isolierter Schleppzeigermechanismus und mechanische Uhr, die einen Chronografenmechanismus mit einem solchen isolierten Schleppzeigermechanismus umfasst
EP3671370A1 (de) 2018-12-20 2020-06-24 Patek Philippe SA Genève Kupplungsvorrichtung und chronographenmechanismus, der eine solche kupplungsvorrichtung umfasst

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