EP4202562A1 - Kupplungsvorrichtung für schaltrad eines uhrwerkmechanismus - Google Patents

Kupplungsvorrichtung für schaltrad eines uhrwerkmechanismus Download PDF

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Publication number
EP4202562A1
EP4202562A1 EP21216840.5A EP21216840A EP4202562A1 EP 4202562 A1 EP4202562 A1 EP 4202562A1 EP 21216840 A EP21216840 A EP 21216840A EP 4202562 A1 EP4202562 A1 EP 4202562A1
Authority
EP
European Patent Office
Prior art keywords
transmission
mobile
elastic bar
coupling device
toothed
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.)
Granted
Application number
EP21216840.5A
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English (en)
French (fr)
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EP4202562B1 (de
Inventor
Didier VUILLEMIN
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.)
Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Publication date
Application filed by Patek Philippe SA Geneve filed Critical Patek Philippe SA Geneve
Priority to EP21216840.5A priority Critical patent/EP4202562B1/de
Publication of EP4202562A1 publication Critical patent/EP4202562A1/de
Application granted granted Critical
Publication of EP4202562B1 publication Critical patent/EP4202562B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/10—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited
    • G04B5/14—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited acting in both directions
    • 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
    • G04B13/00—Gearwork
    • G04B13/005—Gearwork where a revolution in both directions is changed into a revolution in one direction
    • 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
    • G04B27/00—Mechanical devices for setting the time indicating means
    • G04B27/004—Mechanical devices for setting the time indicating means having several simultaneous functions, e.g. stopping or starting the clockwork or the hands

Definitions

  • the present invention relates to a device for coupling a kinematic chain with a toothed mobile in a watch mechanism, the coupling device comprising a slider formed by a reference and a mobile support on which the reference is rotatably mounted.
  • the reference is permanently connected to the kinematic chain, and the support is arranged to move between a first position in which the reference meshes with the toothed mobile and a second position in which the reference is disengaged from the toothed mobile.
  • Coupled designates a connection established between two parts of a machine, generally two shafts, so that the rotation of one causes that of the other.
  • the expression “coupling device” denotes a device enabling the aforementioned connection.
  • Coupling devices for watch mechanisms are already known which comply with the definition given in the preamble. Such coupling devices are used in particular in automatic winding mechanisms to act as horizontal clutches, the return of the slider then fulfilling the function of a clutch wheel.
  • winding of the barrel spring is ensured by an oscillating mass equipped either with a simple clutch allowing the winding of the barrel when the oscillating mass rotates in one of the two directions of rotation, or with an inverted double clutch thanks to which the movements of the oscillating mass always wind up the barrel, regardless of the direction of rotation of the oscillating mass.
  • FIGS. 1A and 1B appended are taken from the work “Théorie d'horlogerie”. These figures are plan views illustrating in a manner schematically an automatic winding mechanism with reversed double clutch whose operation is as follows: whatever the direction of rotation of the oscillating mass 1, the mobiles 6 and 7 must imperatively turn in the direction of the arrow. To do this, use is made of two sliding gears 3 and 4 which are mounted free to pivot on the same small mobile support 5.
  • the mobile support 5 consists of a rocker. Rocker 5 is itself pivotally mounted about an axis which is oriented parallel to the axes of rotation of the two sliding gears and which is located halfway between them.
  • the movable support is not a rocker, but is arranged to slide between two extreme positions.
  • the transmissions 3 and 4 constantly mesh with each other, while also being constantly connected to the pinion 2 of the oscillating mass 1, so that the movements of the oscillating mass cause the two sliding transmissions to rotate in opposite directions. one another.
  • Winding mechanisms that include sliding coupling devices, such as the one just described, are not without problems.
  • the transmission 3 must be constantly in mesh with the pinion 2 of the oscillating mass, while it moves with the rocker 5 which itself pivots around an axis which is not concentric with that of the transmission. .
  • Another problem with these winding mechanisms is that the time required for the reverse double clutch to switch from one configuration to the other is not negligible.
  • the mechanism for winding the figures 1A and 1B further comprises a pawl 8 which is biased against the teeth of the mobile 6 by a spring 9. The function of the pawl 8 is to prevent the mobile 6 from going back during periods when none of the sliding gears 3 and 4 is in taken with him.
  • Coupling devices for watch mechanisms are also used which comply with the definition given in the preamble, in particular in rocker time-setting mechanisms.
  • FIG 2A appended is a diagrammatic representation in plan of a known rocker correction device which is intended to allow the correction of the time and date indications of a timepiece.
  • This figure is taken from the patent document EP 3 486 733 A1 .
  • the device represented comprises a winding stem 11 that is axially movable between a winding position and a time-setting position. It also comprises a correction pinion 13 which is mounted coaxially with the stem, so as to rotate with the latter when it is in the time-setting position.
  • the pinion 13 meshes with a gear train which, in the example shown, is formed by two transmissions 15 and 17 mounted free to rotate.
  • the device shown comprises a player 18 which is formed by a mobile support 19 and a corrector transmission 21 pivotally mounted on the mobile support.
  • the mobile support 19 is constituted by a rocker whose pivot axis (referenced 16) coincides with the axis of rotation of the second reference 17.
  • the corrector return 21 is arranged so as to mesh permanently with the second return 17, so that a kinematic chain connects the rod 11 to the corrector return 21.
  • the rocker correction device of the figure 2A further includes a selector provided to allow a user to control the walkman 18 to selectively mesh the corrective return 21 with a first mobile 23 or with a second mobile 25.
  • a selector provided to allow a user to control the walkman 18 to selectively mesh the corrective return 21 with a first mobile 23 or with a second mobile 25.
  • the corrective idler 21 meshes with the first mobile 23.
  • the configuration in which the corrective idler 21 meshes with the second mobile 25 is not shown.
  • the selector is essentially formed of a bolt 27, accessible from outside the timepiece, and of a positioning lever 29 which comprises two arms which extend on either side of the pivot axis of the lever.
  • the end of one of the arms of the lever 29 is in engagement with the bolt 27, so that the lever rocks in one direction or the other in reaction to the switchings of the bolt.
  • the other arm of the lever 29 ends in a U-shaped fork arranged to receive and to guide between its branches the axis 31 of the corrector transmission 21.
  • the U-shaped fork and the axis 31 together form a sort of articulation which connects the positioning lever 29 to the slider 18. Thanks to the presence of this articulated link, a user has the possibility of causing the correction transmission 21 to mesh selectively with the first mobile 23 or with the second mobile 25 by using the bolt 27 to tilt the positioning lever 29 in one direction or the other.
  • rocker correction devices such as the one just described is not free from problems.
  • the teeth of the corrector return 21 come into abutment against the tops of the teeth of one of the mobiles 23 or 25 instead of being inserted between them. .
  • This situation has the effect of jamming the mechanism, the two teeth being unable to interpenetrate, and the toothed mobiles therefore not being able to mesh with each other.
  • player 18 is blocked in this way before reaching the end of its travel, this blocking has repercussions as far as bolt 27 of the selector, which the user will not fail to feel. Such a situation may encourage the latter to force it at the risk of breaking one of the components of the mechanism.
  • An object of the present invention is to remedy the drawbacks of the prior art which have just been explained.
  • the present invention achieves this and other objects by providing a sliding coupling device which is in accordance with appended claim 1.
  • the coupling device comprises a bistable elastic bar held by its two ends between two anchoring points and working in buckling in a plane perpendicular to the axis of rotation of the transmission.
  • a section of the bistable elastic bar is also fixed to the movable support, so that the position of the latter is slaved to that of the section of the bistable elastic bar.
  • buckling By buckling is meant here the deflection and therefore the deformation of an elastic bar which is held by its ends between two anchoring points and whose undeformed length is greater than the distance between the two anchoring points. Buckling is a deformation in a direction perpendicular to the line passing through the two anchor points.
  • An elastic bar which works in buckling in a given plane of deformation has the possibility of bending in one direction or the other inside this plane, so that a buckled elastic bar has two symmetrical stable configurations (c' is the reason why the elastic bar can be described as "bistable").
  • stable configuration is meant a configuration which is associated with a shape towards which the elastic bar always returns if it is moved away from it by a stress of sufficiently low amplitude.
  • a bistable elastic bar can switch almost instantaneously from one of its stable configurations to another. It will therefore be understood that, thanks to the characteristics of the invention, it is possible to cause the coupling device to switch almost instantaneously.
  • Another advantage of the invention is that the forces associated with the deformations of a bistable elastic bar have the effect of returning the latter to its closest stable configuration. Under these conditions, when the bistable elastic bar is held away from its stable position because the teeth of the transmission abut against those of the toothed mobile, keeping the slider separated from its first position, the bistable elastic bar behaves like a spring which requests the return of the walkman against the teeth of the mobile. It is then sufficient for the toothing of the reference to pivot slightly relative to that of the toothed mobile to unlock the coupling device, the teeth of the reference then lowering spontaneously between those of the mobile.
  • Yet another advantage of the invention is that, because the position of the mobile support is determined by the bistable elastic bar, it is not necessary to provide a fixing of the player to the plate apart from that which is ensured at the level of the anchor points of the bistable elastic blade.
  • the bistable elastic bar works in buckling around a median inflection point, the latter being kept fixed and a median portion of the bistable elastic bar being free to pivot around an axis oriented parallel to the axis of rotation of the transmission and passing through the midpoint of inflection.
  • the coupling device can, advantageously, comprise lateral supports or a pivot member to hold the midpoint of inflection in position.
  • the coupling device comprises a control lever arranged to cooperate with the bistable elastic bar so as to allow it to be switched in one direction or the other between its two stable configurations.
  • the coupling device comprises a control member operable from outside the timepiece comprising the timepiece mechanism, the control member being mechanically connected to the control lever so as to allow a user to switch the coupling device.
  • transmission designates a toothed wheel which is arranged to mesh simultaneously with a driving toothed wheel set and a driven toothed wheel set between which it is interposed.
  • FIG 2B appended is a plan view which schematically illustrates the principle according to which, in accordance with the invention, the position of the player of a time-setting mechanism similar to that of the figure 2A can be slaved to the position of a bistable elastic bar.
  • the coupling device of the time-setting mechanism represented comprises an elastic bar which can be deformed in bending (referenced 33', 33") and two ball joints which are anchored in the plate and arranged to hold the two ends of the elastic bar (only one of the two ball joints, referenced 35, is shown in the figure 2B ).
  • the two ball joints 35 are arranged so as to allow each of the ends of the bistable elastic bar 33', 33" to pivot around an axis of rotation oriented parallel to the axis 31 of the corrective return 21.
  • the undeformed length of the bistable elastic bar 33', 33" is chosen to be greater than the distance separating the axes of rotation around which its ends are arranged to pivot. Under these conditions, as the 33' elastic bar, 33" is much easier to deform in bending than in compression, its rectilinear configuration (not shown) is unstable. The elastic bar 33', 33" is thus led to adopt a buckled configuration in a plane perpendicular to the axis of rotation of the corrective transmission 21, so as to reduce the stresses.
  • the curvature due to the buckling can constitute a deformation of the elastic bar in one direction or the other, so that the elastic bar has two symmetrical fundamental stable configurations (the two fundamental stable configurations are represented in dashed lines in the drawing where they are referenced respectively 33' and 33").
  • the anchoring points of the ends of the bistable elastic bar are on a straight line which passes through the pivot axis 16 of the mobile support 19.
  • the axis 31 of the corrective transmission 21 is also on this same line .
  • a section of the bistable elastic bar 33', 33" is integral with the mobile support 19, so that the position of the latter is slaved to that of the section of the bistable elastic bar.
  • the movable support 19 may for example have on its underside (which is not visible in the Figure 3B ) a pair of pins which project parallel to the pivot axis 16 of the movable support, the pair of pins being in engagement with the section of the bistable elastic bar 33 ', the latter passing between the two pins.
  • the movable support 19 could for example have on its underside a tenon which projects parallel to the pivot axis 16 of the movable support, the tenon being inserted into an eyelet formed of material in a portion of the bistable elastic bar 33 '.
  • THE figures 3A and 3B are two partial plan views of a timepiece mechanism which incorporates a coupling device according to a first embodiment of the invention.
  • the timepiece mechanism in question could for example be the calendar mechanism of a complication timepiece.
  • the illustrated coupling device would serve for example to make it possible to selectively correct the indications of the date and the day of the week.
  • the partial schematic views of the figures 3A and 3B only shows the coupling device.
  • the application to a calendar is only one example among others, and that the coupling device represented lends itself to numerous applications even outside the field of the correction of horological displays.
  • the coupling device represented comprises a slider (generally referenced 37) which is formed of a transmission 39 and a mobile support on which the transmission is rotatably mounted.
  • the reference 39 meshes permanently with a wheel 43 which is part of a kinematic chain (not shown) that includes a watch mechanism.
  • the movable support of player 37 is constituted by a rocker 41 which is arranged to pivot about an axis referenced 45.
  • Rocker 41 is arranged to move between a first position in which transmission 39 meshes with a first toothed mobile 47 so that the slider realizes the coupling between the mobile 47 and the kinematic chain which includes the wheel 43 (as shown in the Figure 3A ) and a second position in which the transmission 39 meshes with a second toothed mobile 49, so that the slider 37 performs the coupling between the mobile 49 and the kinematic chain (as shown in the Figure 3B ). It may be noted that the return 39 is disengaged from the second toothed wheel set 49 when it meshes with the first toothed wheel set 47, and vice versa.
  • the wheel 43 could be the driving mobile, the toothed mobiles 47 and 49 then being two driven mobiles, or conversely, the mobile 43 could be a driven mobile, the toothed mobiles 47 and 49 then being two driving mobiles.
  • the coupling device which is the subject of the present example further comprises a bistable elastic bar (referenced 51) which is arranged to work in buckling around a median point of inflection.
  • the bistable elastic bar 51 may consist for example of two leaf springs of the same length which are arranged to extend in opposite directions from a rigid middle element ( referenced 53).
  • the middle element 53 is in the form of a disc pierced with a central hole (reference 55).
  • the distal ends of the two leaf springs each terminate in a ball joint anchored in the plate (the two ball joints are referenced 57a and 57b).
  • the central hole 55 of the middle element is located at the midpoint of the bistable elastic bar 51.
  • the rigid middle element 53 is fixed on the rocker 41 concentrically to its pivot axis 45, so that the midpoint of the bistable elastic bar 51 (or in other words the central hole 55) is on the pivot axis 45 of the rocker 41. This arrangement allows the rigid middle element 53 to pivot with the rocker 41 around the midpoint.
  • the undeformed length of the bistable elastic bar 51 is chosen to be greater than the distance separating the two ball joints 57a, 57b.
  • the elastic bar 51 is much easier to deform in bending than in compression, its rectilinear configuration (not shown) is unstable.
  • the elastic bar 51 is thus led to adopt a buckled configuration in a plane which is perpendicular to the pivot axis 45 of the mobile support. Since the position of the midpoint of the bistable spring bar 51 is held fixed, the bar is prevented from adopting a first order buckled configuration. It therefore adopts a second-order soaring configuration characterized by the presence of a median point of inflection.
  • the median point of inflection corresponds to the midpoint of the bistable elastic bar 51. In the example illustrated, this point is also located on a straight line which passes through the two ends of the bistable elastic bar.
  • the elastic bar 51 can be in one or the other of two symmetrical stable configurations. These two stable configurations are illustrated respectively in the figures 3A and 3B .
  • the coupling device which is the subject of the present example also comprises a control lever 59 pivoted on an axis 60 and arranged in such a way as to make it possible to switch the bistable elastic bar 51 from one to the other of its two stable setups.
  • one of the arms of the control lever 59 carries a pair of pins which project from its end perpendicular to the plane in which the bistable elastic bar 51 is buckled.
  • a section of the bistable elastic bar passes between the two pins, so that the cooperation between the pair of pins and said section creates an articulated link between the control lever 59 and the bistable elastic bar 51.
  • the switching of the bistable elastic bar also causes the slider 37 to pass from its first to its second position, so that the corrector return 39 s 'deviates from the first toothed mobile 47 and comes into engagement with the second toothed mobile 49 (as shown in the Figure 3B ).
  • THE figures 4A and 4B are partial plan diagrams of an automatic winding mechanism comprising a coupling device according to a second exemplary embodiment of the invention. As explained in more detail below, the coupling device illustrated in the figures 4A and 4B is arranged to fulfill the reversed double clutch function.
  • the automatic winding mechanism of the present example comprises an oscillating weight (referenced 72) and a toothed mobile (referenced 76) which must always be driven in the same direction, whatever the direction of rotation of the oscillating weight.
  • the coupling device of the automatic winding mechanism represented in the figures 4A and 4B comprises a walkman (generally referenced 62) which is formed of a support mobile and two references (respectively referenced 64 and 66) which are mounted crazy on the mobile support.
  • the transmissions 64 and 66 constantly mesh with each other, while also being constantly connected to the pinion (referenced 74) of the oscillating mass 72. It will be understood from the above that the transmissions 64 and 66 rotate in opposite directions. from each other when driven by the oscillating mass.
  • the movable support of player 62 consists of a rocker (referenced 68) which is itself pivotally mounted around an axis (referenced 70).
  • the axis 70 is oriented parallel to the axes of rotation of the two transmissions 64 and 66 and it is arranged halfway between them.
  • Rocker 68 is arranged to move between a first position in which transmission 66 meshes with toothed wheel set 76 (as shown in figure 4A ), the toothed mobile being then driven in the opposite direction to the direction of rotation of the oscillating weight 72, and a second position in which the transmission 64 meshes with the toothed mobile 76 (as shown in the figure 4B ), the toothed mobile being then driven in the direction of rotation of the oscillating mass 72. It can be noted that when the reference 64 meshes with the toothed mobile 76, the reference 66 is disengaged, and that conversely, when the reference with the toothed mobile 76, the reference 64 is disengaged.
  • the coupling device which is the subject of the present example further comprises a bistable elastic bar (referenced 78) which is arranged to work in buckling around a median point of inflection.
  • the bistable elastic bar 78 may consist for example of two leaf springs of the same length which are arranged to extend in opposite directions from a rigid middle element (referenced 80).
  • the middle element 80 is in the form of a disc pierced with a central hole. It can be seen on the other hand that the distal ends of the two leaf springs each terminate in a ball joint anchored in the plate. It will be understood that the central hole of the middle element is located at the midpoint of the bistable elastic bar 78.
  • the rigid middle element 80 is fixed on the rocker 68 concentrically to its pivot axis 70, so that the midpoint of the bistable elastic bar (or in other words the central hole) is on the pivot axis 70. This arrangement allows rigid middle member 80 to pivot with rocker 68 around the midpoint of bistable spring bar 78.
  • the elastic bar 78 can adopt either of two stable symmetrical configurations which are buckled in a plane which is perpendicular to the pivot axis 70 of the player 62. As the position of the midpoint of the bistable elastic bar 78 is kept fixed, the two stable remarkablyd configurations are characterized by the presence of a midpoint of inflection. These two stable configurations are illustrated respectively in the figures 4A and 4B .
  • the pinion 74 exerts a force oriented tangentially on the toothing of the transmission 64. If the oscillating mass rotates clockwise, this force is oriented towards the top of the drawing. In this case, it generates a torque which tends to cause rocker 68 to pivot counterclockwise. As the middle portion 80 of the bistable elastic bar 78 is fixed on the rocker 68, the torque generated by the tangential force is also exerted on the bistable elastic bar. If the latter is in the configuration illustrated in the figure 4A , the additional stress due to this torque has the effect of causing it to pass into the configuration illustrated in the figure 4B . Once the passage of the bistable elastic bar 78 from one stable configuration to the other is initiated, the switching is almost instantaneous and it is then the bistable elastic bar which drives the player.
  • the oscillating mass 72 rotates counterclockwise, the tangential force exerted by the pinion 74 is directed towards the bottom of the drawing. In this case, it generates a torque which tends to cause rocker 68 to pivot clockwise. If the bistable elastic bar is in the configuration shown in the figure 4B , the additional stress due to this torque has the effect of causing it to pass into the configuration illustrated in the figure 4A .
  • An advantage linked to the use of a bistable elastic bar working in buckling around a median inflection point is that its triggering threshold is lower. In other words, the force required to switch the bistable elastic bar is less than the force that would be required if the two stable configurations corresponded to first-order deformations.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
EP21216840.5A 2021-12-22 2021-12-22 Kupplungsvorrichtung für schaltrad eines uhrwerkmechanismus Active EP4202562B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21216840.5A EP4202562B1 (de) 2021-12-22 2021-12-22 Kupplungsvorrichtung für schaltrad eines uhrwerkmechanismus

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Application Number Priority Date Filing Date Title
EP21216840.5A EP4202562B1 (de) 2021-12-22 2021-12-22 Kupplungsvorrichtung für schaltrad eines uhrwerkmechanismus

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EP4202562A1 true EP4202562A1 (de) 2023-06-28
EP4202562B1 EP4202562B1 (de) 2024-08-07

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1029808A (fr) * 1950-08-22 1953-06-08 Bulova Watch Co Inc Montre à remontage automatique par masse oscillante
EP3486733A1 (de) 2017-11-20 2019-05-22 Patek Philippe SA Genève Steuervorrichtung für uhr, die ein schaltrad umfasst
CH716526A2 (fr) * 2019-08-26 2021-02-26 Blancpain Sa Rouage d'horlogerie pour débrayer un train d'engrenage.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1029808A (fr) * 1950-08-22 1953-06-08 Bulova Watch Co Inc Montre à remontage automatique par masse oscillante
EP3486733A1 (de) 2017-11-20 2019-05-22 Patek Philippe SA Genève Steuervorrichtung für uhr, die ein schaltrad umfasst
CH716526A2 (fr) * 2019-08-26 2021-02-26 Blancpain Sa Rouage d'horlogerie pour débrayer un train d'engrenage.

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