EP2871537B1 - Watch with improved power reserve - Google Patents

Watch with improved power reserve Download PDF

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Publication number
EP2871537B1
EP2871537B1 EP13191775.9A EP13191775A EP2871537B1 EP 2871537 B1 EP2871537 B1 EP 2871537B1 EP 13191775 A EP13191775 A EP 13191775A EP 2871537 B1 EP2871537 B1 EP 2871537B1
Authority
EP
European Patent Office
Prior art keywords
movement
ratchet
wheel
winding mechanism
additional
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.)
Active
Application number
EP13191775.9A
Other languages
German (de)
French (fr)
Other versions
EP2871537A1 (en
Inventor
Cédric Decosterd
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.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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 ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP13191775.9A priority Critical patent/EP2871537B1/en
Priority to US14/514,574 priority patent/US9063515B2/en
Priority to JP2014222322A priority patent/JP5844873B2/en
Priority to CN201420679993.5U priority patent/CN204270011U/en
Priority to CN201410638497.XA priority patent/CN104635466B/en
Publication of EP2871537A1 publication Critical patent/EP2871537A1/en
Priority to HK15109565.9A priority patent/HK1208917A1/en
Application granted granted Critical
Publication of EP2871537B1 publication Critical patent/EP2871537B1/en
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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
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • 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
    • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
    • G04B11/022—Devices allowing the motion of a rotatable part in only one direction with a ratchet which makes contact with the rotating member by means of teeth
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • 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
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • G04B13/025—Wheels; Pinions; Spindles; Pivots with elastic means between the toothing and the hub of a toothed wheel
    • 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
    • G04B3/00—Normal winding of clockworks by hand or mechanically; Winding up several mainsprings or driving weights simultaneously
    • G04B3/04—Rigidly-mounted keys, knobs or crowns
    • 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
    • G04B33/00—Calibers
    • G04B33/12—Calibers for extremely long running times
    • 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
    • G04B5/002—Automatic winding up by moving of parts of the clockwork which are not primarily for winding up
    • 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

Definitions

  • the invention relates to a clockwork mechanical movement, comprising at least one energy storage means fed at the input by a ratchet driven by at least one winding mechanism and supplying an output gear train with output.
  • the invention also relates to a timepiece comprising at least one such movement.
  • the invention relates to the field of mechanical clockwork movements.
  • the power reserve of watch mechanisms is a constant concern, and amplified by the number of complications and mechanisms consuming energy on a caliber.
  • To increase the power reserve it is possible to decrease the frequency of the oscillator, or the power at the exhaust, and / or to increase the power available at the barrel or barrels.
  • the available space rarely allows expansion of the barrel, and it must then be restricted to an action on the regulator system.
  • the document FR 1 155 071 A in the name of Nicolet Watch describes a self-winding device for a watch mounted on a vehicle equipped with a speedometer, which includes a gearbox intended to be fixed on the one hand to the end of the cable actuating the speedometer, and secondly to the indicator itself, as well as means connected to this gearbox for transmitting the rotational movement of the cable to the speedometer and the mainspring of the watch.
  • the document WO 2012/168443 A2 In the name of Haute autoimmune Arc / Winkler Pascal describes a source of mechanical energy for watch movement with predefined output torque transmitted to a first mobile of the finishing train.
  • This mechanism comprises a barrel spring whose ends are integral with a shaft and a barrel drum, one of these ends being intended to be kinematically connected to the first mobile of the finishing train.
  • the mechanism comprises a gear train arranged to ensure a kinematic connection between the ends of the mainspring and allow energy transfer between them.
  • the gear train has a planetary gear.
  • This planetary gear includes a first input-output intended to be kinematically connected to a winding mechanism of the mainspring, a second input-output kinematically connected to one end of the mainspring, and a third input-output connected kinematically to the other end of the mainspring.
  • the planetary gear comprises a satellite comprising a non-circular wheel arranged in engagement with a first non-circular sun gear.
  • the object of the invention is to perform a feedback torque in the barrel by a sampling on the work train, to increase the power reserve of an existing movement, reducing the power setting to the exhaust without touch up the basic wheel.
  • the invention relates to a clockwork mechanical movement, comprising at least one energy storage means fed at the input by a ratchet driven by at least one winding mechanism and supplying a finishing gear train, characterized in it comprises first energy harvesting means connected to at least one mobile of said work train by at least a first elastic link forming clutch mechanism, said first power extraction means taking energy from said gear finisher which is powered by said energy storage means, and said first energy harvesting means cooperating with at least one mobile ratchet drive, which movable drive is engaged with said ratchet to supply said means energy storage by reinjection of a portion of the energy taken by said energy sampling means.
  • said at least one mobile ratchet is disengageable under the action of at least one active release mechanism during operation of said at least one winding mechanism.
  • the invention also relates to a timepiece comprising at least one such movement.
  • the object of the invention is to perform a torque reinjection in an energy storage means, in particular at least one cylinder, by a sampling on the work train of a mechanical watch movement 1 of a watch 100, in order to increase the power reserve of an existing movement, decreasing the power setting in the exhaust, without affecting the basic gear.
  • the invention is here described for the non-limiting case where the energy storage means is a cylinder 20. It is understood that the invention is applicable to other energy storage means: several barrels, elastic means linear, physico-chemical transformation of energy by hydrides or the like, or others.
  • the barrel 20 is equipped with a ratchet 3.
  • This ratchet 3 receives energy from a manual winding mechanism 40, or / and an automatic winding mechanism 45, and / or a reinjection mechanism according to the invention, or / and any additional means of energy input, such as solar energy converter, or other, and recharges the cylinder with the energy it receives.
  • the barrel 20 transmits torque to a work train.
  • a first part of this couple is transmitted to a usual exhaust mechanism and not detailed here.
  • a second complementary part of this pair is extracted by first energy harvesting means 6 according to the invention, and transferred to ratchet 3.
  • This reinjection principle seems relatively simple in appearance, because it is sufficient to take a certain torque on the finishing gear and use the excess of this torque to raise the barrel 20. However it involves a number of problems to solve.
  • the torque must be taken as close as possible to the barrel 20 because the efficiency of the system mainly depends on the number of mobiles needed for its operation. If we raise the torque from a fast-rotating wheel, for example the second wheel, it will take a significant multiplicative gear to be able to raise the barrel 20.
  • the ratchet 3 can be driven at any time by a movement of the automatic winding mass 46, oscillating or the like.
  • the mass 46 is, in the embodiment illustrated by the figures, carried by a device frame automatic 15, and a toothing 47 causes the winding through a first inversion wheel 48 and a second inversion wheel 49.
  • the latter impinges a board 17 of a reduction mobile 16 provided with a pinion 18, arranged to drive a toothing 89 of a second wheel 86 of a ratchet drive mobile, specific to the invention, which will be explained later.
  • the manual winding mechanism 40 is automatically disengaged. This implies that for a period of time, the energy provided by the feedback system is lost, until the teeth between the ratchet and the clutch wheel are again engaged. If the watch 100 is worn by a so-called strong carrier (which makes the automatic winding mechanism 45 work a lot), the reinjection system has only a limited influence on the power reserve of the movement, since in this case the reserves of energy are at the maximum level, as long as the watch 100 is worn. In addition, if the system is not engaged, all the torque remains on the gear train. After a while, there is a risk that the amplitude increases until it reaches the rebate.
  • the invention therefore relates to a mechanical watchmaking movement 1 comprising at least one energy storage means 2, in particular a barrel 20.
  • This barrel 20 comprises a drum 21 with a toothing 22, a cover 24, a shaft 25.
  • This energy storage means 2 is fed at the input by a ratchet 3 driven by at least one winding mechanism 4, and it supplies at the output a work train.
  • the ratchet 3 comprises a toothing 31, drive means 23 for cooperating with the shaft 25, and a fastener 32.
  • the finishing gear train conventionally comprises a mobile of average 51 with a pinion 52 and a board 53, a roadway of 54 minutes with a toothing 59, a second mobile 55 with a pinion 56 and a board 57, and a hour wheel 58.
  • the various components of the movement 1 are housed, as the case may be and as visible in the various figures, on a dial support plate 11, a gear train 12, an automatic device lower deck 13, a barrel bridge 14, the automatic device frame 15, a winding bridge 19.
  • this movement 1 comprises first energy harvesting means 6, which are connected to at least one mobile of the work train by at least a first elastic connection 7 forming a disengaging mechanism.
  • These first energy harvesting means 6 cooperate with at least one driving wheel 8 of the ratchet 3, which is engaged with the ratchet 3, to feed the energy storage means 2 by reinjection of a part of the energy taken by the energy harvesting means 6.
  • this at least one driving wheel 8 of the ratchet 3 is disengageable under the action of at least one disengaging mechanism 9 active during operation of the at least one winding mechanism 4.
  • the first elastic link 7, forming a disengaging mechanism, is interposed between the energy taking means 6 and the ratchet 3.
  • the additional intermediate wheel 63 is shown in FIG. figure 9 , in an advantageous embodiment which comprises a recess 630 for the housing of a main spring 67.
  • This spring 67 comprises an outer turn 651 housed in this recess 630 in which it is stopped in pivoting by the engagement of pins 650 of the spring 67 with notches 65 of the wheel 63, or vice versa.
  • the spring 67 comprises at least one spiral strand 654 which joins this outer turn 651 with an inner turn 652, which comprises pivoting stop means 653 on the shaft 68 of the intermediate mobile 60.
  • these stop means 653 are a female square cooperating with a male square 683 of the shaft 68.
  • the geometry of the spring 67, in spiral shape, defined by the calculation is represented by the figure 10 .
  • the coil In order to maximize the number of winding turns of the spring, the coil must be as long as possible while respecting the manufacturing constraints of the "LIGA", in the preferred case of an embodiment of this type.
  • the geometry is optimized so as to guarantee a calculated armature equivalent to about 18 °.
  • the outer point of the attachment of the turn in the center can certainly come in contact with the inner point of the attachment of the turn on the ring (circle wheel), which is not a problem and even allows to partially relieve the stresses in the turn.
  • At least one winding mechanism 4 of the movement 1 is a manual winding mechanism 40 actuated by the user.
  • at least one such driving wheel 8 of the ratchet 3 comprises at least a first additional ratchet drive wheel 82, which is coaxial with a pinion 81 driving the ratchet 3.
  • This first drive wheel of additional ratchet 82, carrier of a toothing 85 arranged to cooperate with the toothing 64 of the additional intermediate wheel 63, is pivotally mounted on a bearing 83 of a shaft 80 that includes the driving wheel 8 of the ratchet 3.
  • the first additional ratchet drive wheel 82 is connected to this shaft 80 by first resiliently rotating return means or at least a first spring 84 constituting such disengaging means 9, during operation of the manual winding mechanism 40 actuated by the user.
  • Such a first additional ratchet drive wheel 82 is visible in the lower part of a more complex mobile illustrated in FIG. figure 11 .
  • the first spring 84 is thus arranged to generate a unidirectional direction of play-free pivoting of the first additional ratchet wheel 82 with respect to the shaft 80 of the driving wheel 8 of the ratchet 3, so that to prevent any transmission of a torque to the gear 5 during a reassembly of the movement 1 by at least one such winding mechanism 4.
  • At least one such winding mechanism 4 is an automatic winding mechanism 45
  • at least one such driving wheel 8 of the ratchet 3 further comprises a second additional ratchet wheel 86, as visible on the figure 11 .
  • This second additional ratchet drive wheel 86, carrier of a toothing 89 arranged to cooperate with the pinion 18 of the reduction wheel 16, is pivotally mounted on a bearing 87 of the shaft 80, and is connected to this shaft 80 by second resilient means of rotation in rotation or at least a second spring 88 constituting such means of 9, during the operation of the automatic winding mechanism 45.
  • it has, on one side of the mobile ratchet drive 8, the feedback system, and on the other side, the automatic winding, which explains the need a clutch release system between the two torque inputs.
  • some of these disengaging means 9 constituted by these second elastically rotating return means or by the at least one second spring 88, exert on the second additional ratchet drive wheel 86 a friction force of which the torque moment is different in the direction of relative pivoting between the disengaging means 9, and the second additional ratchet wheel 86.
  • the second spring 88 is thus arranged to generate a unidirectional direction of play-free pivoting of the second additional ratchet drive wheel 86 with respect to the shaft 80 of the drive wheel 8 of the ratchet 3, so that to prevent any transmission of a torque to the work train during a winding movement 1 by the manual winding mechanism 40 actuated by the user, or during operation of the first energy harvesting means 6.
  • the figure 11 shows the assembled ratchet drive wheel, consisting of five parts: an axle 80, preferably a 20AP steel neck, the first additional ratchet wheel 82 and the second wheel additional ratchet drive 86, which pivot freely, and the first spring 84 and the second spring 88 which ensure the driving or non-driving of these wheels.
  • first additional ratchet drive wheel 82 and the second unidirectional supplementary ratchet wheel 86 preferably made of hardened Beryllium Copper (CuBe), their function is to drive the axis 80 when they undergo a torque from either the automatic winding mechanism 45 or the feedback system. However, they must not transmit torque when they are driven by the axis 80 (disengaging system between the two wheels).
  • the wheel 82 or 86 must have no dead angle, unlike a ratchet wheel, for example.
  • the teeth 85 and 89 of these wheels 82 and 86 are optimized to minimize gearing.
  • each spring 84, 88 according to the direction of the torque applied to it can be simplified in a first "free” direction and a second “friction” drive direction.
  • free direction of the spring there is a small friction between the spring and the wheel concerned, because of a slight preload applied to the spring on its outer diameter, which implies that the wheel will be driven by this weak friction torque, and will turn up to come catch the game with the next wheel or pinion.
  • the two wheels 82 and 86 are preferably designed to receive the same spring, which limits the number of components.
  • their pivot diameters are identical. This allows to have the same size for the attachment of the spring in the center on the drive, including hexagon, axis 80.
  • the first 84 or second 88 flexible spring has the function of driving the axis 80 when working in blocking direction.
  • the axis 80 drives a spring, it should not drive the corresponding wheel.
  • the friction torque is minimized and the locking torque is maximized.
  • the ratchet drive wheel 8 forms a unidirectional wheel whose operation resembles a reversing ratchet wheel.
  • the mobile 8 represents a big progress compared to the known inverters, because it is much less bulky, and therefore easier to implement in the vicinity Immediate ratchet 3.
  • the mobile 8 according to the invention has no blind spot, which allows its mounting in an automatic movement.
  • the Figures 12 to 18 illustrate various non-limiting geometries of springs which are applicable to both the first spring 84 and the second spring 88.
  • the figure 12 shows more particularly the first spring 84 housed in the first additional ratchet drive wheel 82, and the Figures 13 to 18 the second spring 88 housed in the second additional ratchet drive wheel 86.
  • an outer turn 841, respectively 881, of the first spring 84, respectively of the second spring 88 cooperates with a housing 820, respectively 860, of the wheel 82, respectively 86, in which it is held by friction at its periphery or / and lugs 84A, respectively 88A that includes said first spring 84, respectively second spring 88.
  • the inner part of each spring, 842, respectively 882 cooperates with the shaft 80, by a female portion 840, respectively 880, of the first spring 84, respectively of the second spring 88, of complementary profile to a male portion 800 of the shaft 80.
  • the particular profile of the illustrated springs with an asymmetrical stiffness of at least one arm 843, respectively 883, joining the inner part of each spring, 842, respectively 882, to its outer portion 841, respectively 881, makes it possible to apply a torque with a strong moment differential, depending on whether the relative pivoting movement between the shaft 80 and the respective wheel, is in one direction or the other.
  • the ratio of the torque exerted in one direction with respect to the other is greater than 3; depending on the shape of the spring, the sections used, and the pairs of materials present, this ratio can be notably increased, in particular beyond a factor of 10.
  • each spring 842, respectively 882
  • the profile of the spring is closed: the inner part of each spring, 842, respectively 882, has the shape of a rhombus centered on the shaft 80, one of the ends A of the rhombus constitutes the beginning of the outer portion 841, respectively 881, which is circular in almost a complete turn, before winding on itself at point C and forming an arm 843, respectively 883, in a circular sector of about a half-turn, radius less than that of the outer part, clinging to point B at the other end of the symmetrical rhombus at the first end A.
  • the profile of the spring is open: the inner part, 842, respectively 882, has the shape of a disk extended on a radius by a triangle, whose distal tip E is the start of an arm 843, respectively 883, in circular sector of about a half-turn, before winding on itself at the point F and forming the outer portion 841, 881 respectively, which is circular in almost a complete turn, radius greater than that of the arm, before stopping at a distal end G.
  • the profile of the spring is open: the inner part, 842, respectively 882, has the shape of a disk extended on a radius by a triangle, whose distal tip H constitutes the departure of an arm 843, respectively 883, in spiral increasing about half a turn to the point I where starts an outer portion 841, respectively 881, circular, before stopping at a distal end J, after about a turn and a quarter with respect to the point H.
  • the profile of the spring is open, the spring having two symmetrical strands: the inner part, 842, respectively 882, has the shape of a disk which is hooked in K, N, an arm 843, respectively 883, spiraling increasing about three quarters of a turn to the point L, P, where starts an outer portion 841, respectively 881, circular one-half turn, before stopping at a distal end M, Q.
  • the profile of the spring is closed, and comprises a mesh with a pitch of 120 °: the inner part, 842, respectively 882, has the shape of a disc whose part R at the point R an arm 843, respectively 883, substantially radial but curved, which joins at point S a rope 885 which joins two circular sectors of larger diameter, one sector TU forming an outer portion 841, respectively 881, the spring starting at point U on another rope 885 making about 120 ° with the previous, and joining at point V another radial arc similar to the first, the point V being the conjugate of the starting point S.
  • the profile of the spring is open, the spring having two symmetrical strands: the inner part, 842, respectively 882, has the shape of a disk which is engaged in W a radial arm 886 of strong section, up to a point X of which part at right angle arm 843, respectively 883, of less section than the radial arm 886, to a distal end Y periphery of the wheel.
  • the main spring 67 of the intermediate wheel 60 is advantageously dimensioned and arranged to catch the clearance between the additional intermediate wheel 63 and this additional ratchet wheel 82.
  • the movement 1 comprises at least one balance regulator member, and the energy picking means 6 take a constant mechanical torque on the work train when this regulating member is operating.
  • this balance is dimensioned more weakly than would be the same such movement 1 devoid of energy harvesting means 6, so as to maintain a sufficient oscillation amplitude to its proper operation.
  • the movement 1 comprises at least one balance-regulating member, and at least one such winding mechanism 4 is an automatic winding mechanism 45, and the energy-taking means 6 take a constant mechanical torque. on the work train only when the movement 1 is maintained in a fixed position in space and when the automatic winding mechanism 45 is inactive, so as to then reduce the amplitude of oscillation of the balance and to increase the reserve of movement walk 1.
  • the winding mechanism 4 comprises a manual winding mechanism 40, which comprises a rod 41 actuated by the user and which is arranged to drive, in an axial position of winding of the rod 41 and in a winding rotation direction which is printed to it by the user, a sliding pinion 43 arranged to mesh with a winding pinion 42 driving a crown wheel 44 meshing with the ratchet 3.
  • the wheel crown 44 is arranged to cooperate with a pawl 31 comprising means of catching gear between the ratchet 3 and the crown wheel 44 during a maneuver of the rod 41.
  • the invention also relates to a timepiece 100, in particular a watch, comprising at least one such movement.
  • the mechanism according to the invention must catch the game created in the reinjection system under the action of the automatic winding, before continuing to drive the ratchet, while avoiding all the torque passes through the finishing train and causes then the reshuffles. This is possible when the torque take on the finishing gear is constant when the movement is running. As regards the energy level, then decreases the power required for the balance, by the constant torque torque of the finishing gear. This implies a downsizing of the pendulum, to ensure a satisfactory amplitude.
  • the dimensioning of the balance corresponds directly to the reduction of torque taken by the reinjection system.
  • the amplitude of the pendulum will decrease proportionally to the torque taken for reinjection. But in this case, the decrease in amplitude, which slightly alters the chronometric performance of the watch during a period of non-use, allows to spend several days without stopping the movement, which would be impossible without the reinjection system according to the invention.
  • the gear set retrofit system makes it possible to compensate for the backlash caused during automatic winding, which makes it possible to ensure permanent contact with the toothing of the ratchet even when it is driven.
  • the use of a unidirectional wheel without play at the intermediate mobile 60 is a good solution: it turns freely in one direction and blocks in the other, all with a very low dead angle.
  • Regarding the gear set it is still possible to use a tooth geometry with a reduced clearance, or a no-play toothing comprising flexible teeth elements.
  • the solution without blind spots maximizes efficiency in a self-winding movement.
  • the release system by a unidirectional wheel meets the requirements of simplicity of implementation and realization. This makes it possible to limit the number of components and their complexity.
  • the catch-up and blocking features are each time provided directly by a single component.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Measurement Of Unknown Time Intervals (AREA)

Description

Domaine de l'inventionField of the invention

L'invention concerne un mouvement mécanique d'horlogerie, comportant au moins un moyen de stockage d'énergie alimenté en entrée par un rochet entraîné par au moins un mécanisme de remontage et alimentant en sortie un rouage de finissage.The invention relates to a clockwork mechanical movement, comprising at least one energy storage means fed at the input by a ratchet driven by at least one winding mechanism and supplying an output gear train with output.

L'invention concerne encore une pièce d'horlogerie comportant au moins un tel mouvement.The invention also relates to a timepiece comprising at least one such movement.

L'invention concerne le domaine des mouvements mécaniques d'horlogerie.The invention relates to the field of mechanical clockwork movements.

Arrière-plan de l'inventionBackground of the invention

La réserve de marche des mécanismes d'horlogerie est une préoccupation constante, et amplifiée par le nombre de complications et de mécanismes consommateurs d'énergie sur un calibre. Pour augmenter la réserve de marche, on peut diminuer la fréquence de l'oscillateur, ou la puissance à l'échappement, ou/et augmenter la puissance disponible au niveau du ou des barillets. Dans tous les cas, il faut changer le rouage de finissage, le réglage, ainsi que le ressort de barillet, ce qui représente une modification importante, et coûteuse, d'un calibre existant. De plus, l'espace disponible permet rarement une extension du barillet, et il faut alors se restreindre à une action sur le système régulateur.The power reserve of watch mechanisms is a constant concern, and amplified by the number of complications and mechanisms consuming energy on a caliber. To increase the power reserve, it is possible to decrease the frequency of the oscillator, or the power at the exhaust, and / or to increase the power available at the barrel or barrels. In all cases, it is necessary to change the finishing gear, the adjustment, as well as the mainspring, which represents a significant modification, and expensive, of an existing caliber. In addition, the available space rarely allows expansion of the barrel, and it must then be restricted to an action on the regulator system.

Le document FR 1 155 071 A au nom de Nicolet Watch décrit un dispositif de remontage automatique pour montre montée sur un véhicule muni d'un indicateur de vitesse, qui comporte une boîte d'engrenages destinée à être fixée, d'une part à l'extrémité du câble actionnant l'indicateur de vitesse, et d'autre part à l'indicateur lui-même, ainsi que des moyens reliés à cette boîte d'engrenages pour transmettre le mouvement de rotation du câble à l'indicateur de vitesse et au ressort moteur de la montre.The document FR 1 155 071 A in the name of Nicolet Watch describes a self-winding device for a watch mounted on a vehicle equipped with a speedometer, which includes a gearbox intended to be fixed on the one hand to the end of the cable actuating the speedometer, and secondly to the indicator itself, as well as means connected to this gearbox for transmitting the rotational movement of the cable to the speedometer and the mainspring of the watch.

Le document WO 2012/168443 A2 au nom de Haute Ecole Arc / Winkler Pascal décrit une source d'énergie mécanique pour mouvement horloger à couple de sortie prédéfini transmis à un premier mobile du rouage de finissage. Ce mécanisme comporte un ressort de barillet dont les extrémités sont solidaires d'un arbre et d'un tambour de barillet, l'une de ces extrémités étant destinée à être reliée cinématiquement au premier mobile du rouage de finissage. Le mécanisme comporte un train d'engrenages agencé pour assurer une liaison cinématique entre les extrémités du ressort de barillet et permettre un transfert d'énergie entre elles. Le train d'engrenages comporte un train planétaire. Ce train planétaire comporte une première entrée-sortie destinée à être reliée cinématiquement à un mécanisme de remontage du ressort de barillet, une seconde entrée-sortie reliée cinématiquement à une extrémité du ressort de barillet, et une troisième entrée-sortie reliée cinématiquement à l'autre extrémité du ressort de barillet. Le train planétaire comporte un satellite comportant une roue non circulaire agencée en prise avec une première roue solaire non circulaire.The document WO 2012/168443 A2 In the name of Haute Ecole Arc / Winkler Pascal describes a source of mechanical energy for watch movement with predefined output torque transmitted to a first mobile of the finishing train. This mechanism comprises a barrel spring whose ends are integral with a shaft and a barrel drum, one of these ends being intended to be kinematically connected to the first mobile of the finishing train. The mechanism comprises a gear train arranged to ensure a kinematic connection between the ends of the mainspring and allow energy transfer between them. The gear train has a planetary gear. This planetary gear includes a first input-output intended to be kinematically connected to a winding mechanism of the mainspring, a second input-output kinematically connected to one end of the mainspring, and a third input-output connected kinematically to the other end of the mainspring. The planetary gear comprises a satellite comprising a non-circular wheel arranged in engagement with a first non-circular sun gear.

Résumé de l'inventionSummary of the invention

Le but de l'invention est d'effectuer une réinjection de couple dans le barillet par un prélèvement sur le rouage de finissage, afin d'augmenter la réserve de marche d'un mouvement existant, en diminuant la puissance réglant à l'échappement sans retoucher le rouage de base.The object of the invention is to perform a feedback torque in the barrel by a sampling on the work train, to increase the power reserve of an existing movement, reducing the power setting to the exhaust without touch up the basic wheel.

A cet effet, l'invention concerne un mouvement mécanique d'horlogerie, comportant au moins un moyen de stockage d'énergie alimenté en entrée par un rochet entraîné par au moins un mécanisme de remontage et alimentant en sortie un rouage de finissage, caractérisé en ce qu'il comporte des premiers moyens de prélèvement d'énergie reliés à au moins un mobile dudit rouage de finissage par au moins une première liaison élastique formant mécanisme de débrayage, lesdits premiers moyens de prélèvement d'énergie prélevant de l'énergie dudit rouage de finissage lequel est alimenté par ledit moyen de stockage d'énergie, et lesdits premiers moyens de prélèvement d'énergie coopérant avec au moins un mobile d'entraînement du rochet, lequel mobile d'entraînement est en prise avec ledit rochet pour alimenter ledit moyen de stockage d'énergie par réinjection d'une partie de l'énergie prélevée par lesdits moyens de prélèvement d'énergie.For this purpose, the invention relates to a clockwork mechanical movement, comprising at least one energy storage means fed at the input by a ratchet driven by at least one winding mechanism and supplying a finishing gear train, characterized in it comprises first energy harvesting means connected to at least one mobile of said work train by at least a first elastic link forming clutch mechanism, said first power extraction means taking energy from said gear finisher which is powered by said energy storage means, and said first energy harvesting means cooperating with at least one mobile ratchet drive, which movable drive is engaged with said ratchet to supply said means energy storage by reinjection of a portion of the energy taken by said energy sampling means.

Selon une caractéristique de l'invention, ledit au moins un mobile d'entraînement du rochet est débrayable sous l'action d'au moins un mécanisme de débrayage actif lors du fonctionnement dudit au moins un mécanisme de remontage.According to a feature of the invention, said at least one mobile ratchet is disengageable under the action of at least one active release mechanism during operation of said at least one winding mechanism.

L'invention concerne encore une pièce d'horlogerie comportant au moins un tel mouvement.The invention also relates to a timepiece comprising at least one such movement.

Description sommaire des dessinsBrief description of the drawings

D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée qui va suivre, en référence aux dessins annexés, où :

  • la figure 1 représente, de façon schématisée et en vue en plan, une montre comportant un mouvement mécanique, lequel comporte un accumulateur d'énergie mécanique sous forme d'un barillet, et un mécanisme régulateur, ce mouvement étant à réserve de marche améliorée avec un mécanisme de réinjection d'énergie selon l'invention ;
  • la figure 2 représente, de façon schématisée, partielle et en coupe selon le tracé EE, le mouvement de la figure 1, et montre en particulier le rouage de finissage ;
  • la figure 3 représente, de façon schématisée, partielle et en coupe selon le tracé BB, le mouvement de la figure 1, et montre en particulier le rouage automatique ;
  • la figure 4 représente, de façon schématisée, partielle et en coupe selon le tracé DD, le mouvement de la figure 1, et montre en particulier le remontage manuel;
  • la figure 5 représente, de façon schématisée, partielle et en coupe selon le tracé FF, le mouvement de la figure 1, et montre en particulier le mécanisme de réinjection ;
  • la figure 6 représente, de façon schématisée, partielle et en coupe selon le tracé AA, le mouvement de la figure 1, et montre en particulier le mobile d'entraînement du rochet ;
  • la figure 7 représente, de façon schématisée, partielle et en coupe selon le tracé CC, le mouvement de la figure 1, et montre en particulier le rouage du mécanisme de réinjection ;
  • la figure 8 représente, de façon schématisée et en perspective, un mobile intermédiaire que comporte le mécanisme de réinjection d'énergie, ce mobile intermédiaire comportant une roue intermédiaire partiellement libre en pivotement liée par des moyens de rappel élastique à un arbre solidaire d'un premier pignon ;
  • la figure 9 représente, de façon schématisée et en perspective, la roue intermédiaire de la figure 8 ;
  • la figure 10 représente, de façon schématisée et en perspective, la roue intermédiaire de la figure 8 équipée de ses moyens de rappel élastique vers une position angulaire de repos par rapport à l'arbre ;
  • la figure 11 représente, de façon schématisée et en perspective, un mobile d'entraînement rochet assemblé selon l'invention, comportant, de part et d'autre d'un arbre une première roue partiellement libre en pivotement liée par des moyens de rappel élastique à cet arbre, et une deuxième roue également partiellement libre en pivotement liée par des moyens de rappel élastique au même arbre ;
  • les figures 12 à 18 représentent, de façon schématisée et en plan, différentes variantes des moyens de rappel élastique équipant la première roue ou/et la deuxième roue de la figure 11 ;
  • la figure 19 représente, sous forme d'un schéma-blocs, le système de réinjection d'énergie selon l'invention.
Other features and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, in which:
  • the figure 1 schematically and in plan view, a watch comprising a mechanical movement, which comprises a mechanical energy accumulator in the form of a barrel, and a regulating mechanism, this movement being in an improved power reserve with a mechanical mechanism. reinjection of energy according to the invention;
  • the figure 2 represents, schematically, partially and in section along the EE line, the movement of the figure 1 , and shows in particular the finishing gear;
  • the figure 3 represents, schematically, partially and in section along the line BB, the movement of the figure 1 , and shows in particular the automatic gear;
  • the figure 4 represents, schematically, partially and in section along the DD line, the movement of the figure 1 , and in particular shows manual winding;
  • the figure 5 represents, schematically, partially and in section along the FF line, the movement of the figure 1 , and shows in particular the feedback mechanism;
  • the figure 6 represents, schematically, partially and in section along the AA line, the movement of the figure 1 , and shows in particular the mobile ratchet drive;
  • the figure 7 represents, schematically, partially and in section along the CC line, the movement of the figure 1 , and shows in particular the cog of the feedback mechanism;
  • the figure 8 represents schematically and in perspective, an intermediate mobile that includes the energy feedback mechanism, the intermediate mobile having an intermediate wheel free pivotally connected by elastic return means to a shaft secured to a first pinion;
  • the figure 9 represents, schematically and in perspective, the intermediate wheel of the figure 8 ;
  • the figure 10 represents, schematically and in perspective, the intermediate wheel of the figure 8 equipped with its elastic return means to an angular position of rest relative to the shaft;
  • the figure 11 represents, diagrammatically and in perspective, an assembled ratchet drive according to the invention, comprising, on either side of a shaft, a first partially free wheel pivotally connected by elastic return means to this shaft and a second wheel also partially free pivotally connected by elastic return means to the same shaft;
  • the Figures 12 to 18 represent, schematically and in plan, different variants of the elastic return means equipping the first wheel and / or the second wheel of the figure 11 ;
  • the figure 19 represents, in the form of a block diagram, the energy reinjection system according to the invention.

Description détaillée des modes deDetailed description of the modes of réalisation préféréspreferred embodiments

Le but de l'invention est d'effectuer une réinjection de couple dans un moyen de stockage d'énergie, notamment au moins un barillet, par un prélèvement sur le rouage de finissage d'un mouvement 1 d'horlogerie mécanique d'une montre 100, afin d'augmenter la réserve de marche d'un mouvement existant, en diminuant la puissance réglant à l'échappement, sans pour autant retoucher le rouage de base.The object of the invention is to perform a torque reinjection in an energy storage means, in particular at least one cylinder, by a sampling on the work train of a mechanical watch movement 1 of a watch 100, in order to increase the power reserve of an existing movement, decreasing the power setting in the exhaust, without affecting the basic gear.

Par simplification l'invention est ici décrite pour le cas non limitatif où le moyen de stockage d'énergie est un barillet 20. On comprend que l'invention est applicable à d'autres moyens de stockage d'énergie : plusieurs barillets, moyens élastiques linéaires, transformation physico-chimique d'énergie par hydrures ou similaires, ou autres.For simplification the invention is here described for the non-limiting case where the energy storage means is a cylinder 20. It is understood that the invention is applicable to other energy storage means: several barrels, elastic means linear, physico-chemical transformation of energy by hydrides or the like, or others.

Pour diminuer la puissance à l'échappement, il est en effet théoriquement possible de prélever une partie du couple directement sur le rouage de finissage. Ce couple supplémentaire peut être directement réinjecté dans le barillet afin d'augmenter sa capacité.To reduce the power at the exhaust, it is theoretically possible to take a portion of the torque directly on the gear train. This additional torque can be directly reinjected into the barrel to increase its capacity.

Le barillet 20 est équipé d'un rochet 3. Ce rochet 3 reçoit de l'énergie d'un mécanisme de remontage manuel 40, ou/et d'un mécanisme de remontage automatique 45, ou/et d'un mécanisme de réinjection selon l'invention, ou/et de tout moyen supplémentaire d'apport d'énergie, tel que convertisseur d'énergie solaire, ou autre, et recharge le barillet avec cette énergie qu'il reçoit.The barrel 20 is equipped with a ratchet 3. This ratchet 3 receives energy from a manual winding mechanism 40, or / and an automatic winding mechanism 45, and / or a reinjection mechanism according to the invention, or / and any additional means of energy input, such as solar energy converter, or other, and recharges the cylinder with the energy it receives.

Le barillet 20 transmet du couple à un rouage de finissage. Une première partie de ce couple est transmise à un mécanisme d'échappement usuel et non détaillé ici. Une deuxième partie complémentaire de ce couple est extraite par des premiers moyens de prélèvement d'énergie 6 selon l'invention, et transférée au rochet 3.The barrel 20 transmits torque to a work train. A first part of this couple is transmitted to a usual exhaust mechanism and not detailed here. A second complementary part of this pair is extracted by first energy harvesting means 6 according to the invention, and transferred to ratchet 3.

Ce principe de réinjection semble relativement simple en apparence, car il suffit de prélever un certain couple sur le rouage de finissage et d'utiliser l'excédent de ce couple pour remonter le barillet 20. Toutefois il implique un certain nombre de problèmes à résoudre.This reinjection principle seems relatively simple in appearance, because it is sufficient to take a certain torque on the finishing gear and use the excess of this torque to raise the barrel 20. However it involves a number of problems to solve.

Tout d'abord, le couple doit être prélevé le plus près possible du barillet 20 car le rendement du système dépend surtout du nombre de mobiles nécessaires à son fonctionnement. Si on remonte le couple depuis une roue à rotation rapide, par exemple la roue seconde, il faudra un rouage multiplicatif important pour pouvoir remonter le barillet 20.First, the torque must be taken as close as possible to the barrel 20 because the efficiency of the system mainly depends on the number of mobiles needed for its operation. If we raise the torque from a fast-rotating wheel, for example the second wheel, it will take a significant multiplicative gear to be able to raise the barrel 20.

Dans un mouvement 1 classique, le couple sur le rouage est transmis par le tambour 21 du barillet 20. Il n'est donc pas possible de réinjecter du couple par la denture 22 du tambour 20, car la vitesse est définie par l'échappement et la démultiplication du rouage de finissage. Il est donc nécessaire de réinjecter le couple directement par le rochet 3. De ce fait, il faut installer un système unidirectionnel ou débrayable entre le rouage du système de réinjection et le rochet 3. Faute d'un tel système assurant la sécurité, lors d'un remontage manuel ou automatique, le couple donné sur le rochet 3 serait transmis directement sur le rouage par le système de réinjection, ce qui provoquerait une augmentation du couple sur l'échappement, entraînant une augmentation massive de l'amplitude et du rebat.In a conventional movement 1, the torque on the gear is transmitted by the drum 21 of the barrel 20. It is therefore not possible to reinject torque through the toothing 22 of the drum 20, because the speed is defined by the exhaust and the gearing of the finishing gear. It is therefore necessary to reinject the torque directly by the ratchet 3. Therefore, it is necessary to install a unidirectional or disengageable system between the gear of the reinjection system and the ratchet 3. In the absence of such a system ensuring safety, when a manual or automatic winding, the torque given on the ratchet 3 would be transmitted directly to the train by the feedback system, which would cause an increase in torque on the exhaust, resulting in a massive increase in amplitude and rebate.

Dans le cas d'un mouvement 1 avec un mécanisme de remontage automatique 45, le rochet 3 peut être entraîné à tout moment par un mouvement de la masse de remontage automatique 46, oscillante ou similaire. La masse 46 est, dans la réalisation illustrée par les figures, portée par un bâti dispositif automatique 15, et une denture 47 entraîne le remontage au travers d'une première roue d'inversion 48 et d'une deuxième roue d'inversion 49. Cette dernière attaque une planche 17 d'un mobile de réduction 16 muni d'un pignon 18, agencé pour entraîner une denture 89 d'une deuxième roue 86 d'un mobile d'entraînement de rochet, propre à l'invention, qui va être exposé plus loin.In the case of a movement 1 with an automatic winding mechanism 45, the ratchet 3 can be driven at any time by a movement of the automatic winding mass 46, oscillating or the like. The mass 46 is, in the embodiment illustrated by the figures, carried by a device frame automatic 15, and a toothing 47 causes the winding through a first inversion wheel 48 and a second inversion wheel 49. The latter impinges a board 17 of a reduction mobile 16 provided with a pinion 18, arranged to drive a toothing 89 of a second wheel 86 of a ratchet drive mobile, specific to the invention, which will be explained later.

A ce moment, le mécanisme de remontage manuel 40 est automatiquement débrayé. Cela implique que durant un certain temps, l'énergie apportée par le système de réinjection est perdue, jusqu'à ce que les dentures entre le rochet et la roue de débrayage soient à nouveau en prise. Si la montre 100 est portée par un porteur dit fort (qui fait beaucoup fonctionner le mécanisme de remontage automatique 45), le système de réinjection n'a qu'une influence limitée sur la réserve de marche du mouvement, puisque dans ce cas les réserves d'énergie sont au niveau maximal, tant que la montre 100 est portée. De plus, si le système n'est pas en prise, tout le couple reste sur le rouage de finissage. Après un certain temps, il y a un risque que l'amplitude augmente jusqu'à atteindre le rebat.At this time, the manual winding mechanism 40 is automatically disengaged. This implies that for a period of time, the energy provided by the feedback system is lost, until the teeth between the ratchet and the clutch wheel are again engaged. If the watch 100 is worn by a so-called strong carrier (which makes the automatic winding mechanism 45 work a lot), the reinjection system has only a limited influence on the power reserve of the movement, since in this case the reserves of energy are at the maximum level, as long as the watch 100 is worn. In addition, if the system is not engaged, all the torque remains on the gear train. After a while, there is a risk that the amplitude increases until it reaches the rebate.

Les points mentionnés ci-dessus démontrent bien la complexité de ce système de réinjection.The points mentioned above demonstrate the complexity of this reinjection system.

L'intégration d'un mécanisme de réinjection de couple dans un mouvement 1 à mécanisme de remontage manuel 40 est tout à fait justifiée, car le gain en réserve de marche est directement observé par l'utilisateur. De plus, le système de réinjection est toujours en prise avec le rochet 3, sauf à l'instant du remontage par une tige 41. En principe, un utilisateur possédant un mouvement manuel remonte sa montre seulement 3 à 4 fois par semaine, en fonction de la réserve de marche de celle-ci. La perte d'énergie potentielle durant cette période n'est donc pas perceptible.The integration of a torque feedback mechanism in a movement 1 manual winding mechanism 40 is entirely justified, because the power reserve is directly observed by the user. In addition, the reinjection system is still engaged with the ratchet 3, except at the time of reassembly by a rod 41. In principle, a user with a manual movement back his watch only 3 to 4 times a week, depending of the power reserve of this one. The loss of potential energy during this period is therefore not perceptible.

L'intégration d'un mécanisme de réinjection de couple dans un mouvement 1 à mécanisme de remontage automatique 45 est utile lorsque la montre 100 n'est pas portée, par exemple si elle est déposée pendant plusieurs jours durant le week-end. A ce moment, une augmentation de la réserve de marche est appréciable afin de ne pas devoir remonter sa montre le lundi matin.The integration of a torque feedback mechanism in a movement 1 with automatic winding mechanism 45 is useful when the watch 100 is not worn, for example if it is deposited for several days during the weekend. At this moment, an increase of the power reserve is appreciable so as not to have to put up his watch on Monday morning.

L'architecture du mécanisme selon l'invention est présentée ci-dessous, les justifications de calcul seront présentées dans la suite de l'exposé.The architecture of the mechanism according to the invention is presented below, the calculation justifications will be presented later in the presentation.

L'invention concerne donc un mouvement mécanique 1 d'horlogerie, comportant au moins un moyen de stockage d'énergie 2, notamment un barillet 20. Ce barillet 20 comporte un tambour 21 avec une denture 22, un couvercle 24, un arbre 25.The invention therefore relates to a mechanical watchmaking movement 1 comprising at least one energy storage means 2, in particular a barrel 20. This barrel 20 comprises a drum 21 with a toothing 22, a cover 24, a shaft 25.

Ce moyen de stockage d'énergie 2 est alimenté en entrée par un rochet 3 entraîné par au moins un mécanisme de remontage 4, et il alimente en sortie un rouage de finissage. Le rochet 3 comporte une denture 31, des moyens d'entraînement 23 pour coopérer avec l'arbre 25, et une fixation 32. Le rouage de finissage comporte classiquement un mobile de moyenne 51 avec un pignon 52 et une planche 53, une chaussée des minutes 54 avec une denture 59, un mobile de seconde 55 avec un pignon 56 et une planche 57, et une roue des heures 58.This energy storage means 2 is fed at the input by a ratchet 3 driven by at least one winding mechanism 4, and it supplies at the output a work train. The ratchet 3 comprises a toothing 31, drive means 23 for cooperating with the shaft 25, and a fastener 32. The finishing gear train conventionally comprises a mobile of average 51 with a pinion 52 and a board 53, a roadway of 54 minutes with a toothing 59, a second mobile 55 with a pinion 56 and a board 57, and a hour wheel 58.

Les différents composants du mouvement 1 sont logés, selon le cas et tel que visible sur les différentes figures, sur une platine d'appui cadran 11, un pont de rouage 12, un pont inférieur de dispositif automatique 13, un pont de barillet 14, le bâti de dispositif automatique 15, un pont de remontoir 19.The various components of the movement 1 are housed, as the case may be and as visible in the various figures, on a dial support plate 11, a gear train 12, an automatic device lower deck 13, a barrel bridge 14, the automatic device frame 15, a winding bridge 19.

Selon l'invention, ce mouvement 1 comporte des premiers moyens de prélèvement d'énergie 6, lesquels sont reliés à au moins un mobile du rouage de finissage par au moins une première liaison élastique 7 formant mécanisme de débrayage.According to the invention, this movement 1 comprises first energy harvesting means 6, which are connected to at least one mobile of the work train by at least a first elastic connection 7 forming a disengaging mechanism.

Ces premiers moyens de prélèvement d'énergie 6 coopèrent avec au moins un mobile d'entraînement 8 du rochet 3 , lequel est en prise avec le rochet 3, pour alimenter le moyen de stockage d'énergie 2 par réinjection d'une partie de l'énergie prélevée par les moyens de prélèvement d'énergie 6.These first energy harvesting means 6 cooperate with at least one driving wheel 8 of the ratchet 3, which is engaged with the ratchet 3, to feed the energy storage means 2 by reinjection of a part of the energy taken by the energy harvesting means 6.

Avantageusement, cet au moins un mobile d'entraînement 8 du rochet 3 est débrayable sous l'action d'au moins un mécanisme de débrayage 9 actif lors du fonctionnement du au moins un mécanisme de remontage 4.Advantageously, this at least one driving wheel 8 of the ratchet 3 is disengageable under the action of at least one disengaging mechanism 9 active during operation of the at least one winding mechanism 4.

De façon avantageuse, la première liaison élastique 7, formant mécanisme de débrayage, est interposée entre les moyens de prélèvement d'énergie 6 et le rochet 3.Advantageously, the first elastic link 7, forming a disengaging mechanism, is interposed between the energy taking means 6 and the ratchet 3.

Selon l'invention les moyens de prélèvement d'énergie 6 sont situés, en aval du moyen de stockage d'énergie 2, au niveau d'au moins un mobile intermédiaire 60. Ce mobile intermédiaire 60, illustré à la figure 8, comporte, coaxiales autour d'un arbre 68, et de part et d'autre d'un premier pignon 61 entraîné par le moyen de stockage d'énergie 2, en particulier la denture 22 d'un tambour 21 d'un barillet 20 :

  • - d'une part une roue intermédiaire 62 de liaison avec un mobile du rouage de finissage, cette roue intermédiaire 62 étant solidaire en pivotement du premier pignon 61,
  • - -et d'autre part une roue intermédiaire supplémentaire 63 de liaison, comportant une denture 64, et engrenant avec un tel mobile d'entraînement 8 du rochet 3 , la roue intermédiaire supplémentaire 63 étant montée pivotante sur un arbre 68 que comporte le mobile intermédiaire 60 et liée à cet arbre 68 par des moyens de rappel élastique en rotation ou au moins un ressort principal 67 constituant la première liaison élastique 7 et inséré dans un logement 65 de la roue 63 et dans un logement 66 du mobile intermédiaire 60.
According to the invention, the energy harvesting means 6 are situated, downstream of the energy storage means 2, at the level of at least one intermediate mobile 60. This intermediate mobile 60, illustrated in FIG. figure 8 , comprises, coaxial around a shaft 68, and on both sides of a first pinion 61 driven by the energy storage means 2, in particular the toothing 22 of a drum 21 of a barrel 20:
  • - On the one hand an intermediate wheel 62 connecting with a mobile of the work train, this intermediate wheel 62 being integral in pivoting of the first gear 61,
  • - And secondly an additional intermediate wheel 63 connection, having a toothing 64, and meshing with such a drive wheel 8 of the ratchet 3, the additional intermediate wheel 63 being pivotally mounted on a shaft 68 that includes the mobile intermediate 60 and connected to this shaft 68 by means of resilient return in rotation or at least one main spring 67 constituting the first elastic connection 7 and inserted into a housing 65 of the wheel 63 and in a housing 66 of the intermediate mobile 60.

La roue intermédiaire supplémentaire 63 est représentée à la figure 9, dans une réalisation avantageuse qui comporte un chambrage 630 pour le logement d'un ressort principal 67. Ce ressort 67 comporte une spire externe 651 logée dans ce chambrage 630 dans lequel elle est arrêtée en pivotement par la coopération d'ergots 650 du ressort 67 avec des encoches 65 de la roue 63, ou inversement. Le ressort 67 comporte au moins un brin en 654 en spirale qui joint cette spire externe 651 avec une spire interne 652, laquelle comporte des moyens d'arrêt en pivotement 653 sur l'arbre 68 du mobile intermédiaire 60. Ici ces moyens d'arrêt 653 sont un carré femelle coopérant avec un carré mâle 683 de l'arbre 68. Lors de son fonctionnement, la roue intermédiaire supplémentaire 63 pivote librement sur l'axe 68 de la roue intermédiaire 62, entraînée par le ressort 67 dont la spire interne 652 est ainsi fixement liée à l'axe 68 du mobile 60.The additional intermediate wheel 63 is shown in FIG. figure 9 , in an advantageous embodiment which comprises a recess 630 for the housing of a main spring 67. This spring 67 comprises an outer turn 651 housed in this recess 630 in which it is stopped in pivoting by the engagement of pins 650 of the spring 67 with notches 65 of the wheel 63, or vice versa. The spring 67 comprises at least one spiral strand 654 which joins this outer turn 651 with an inner turn 652, which comprises pivoting stop means 653 on the shaft 68 of the intermediate mobile 60. Here these stop means 653 are a female square cooperating with a male square 683 of the shaft 68. During its operation, the additional intermediate wheel 63 pivots freely on the axis 68 of the intermediate wheel 62, driven by the spring 67 whose inner turn 652 is thus fixedly connected to the axis 68 of the mobile 60.

La géométrie du ressort 67, en forme spirale, définie par le calcul est représentée par la figure 10. Afin de maximiser le nombre de tours d'armage du ressort, la spire doit être aussi longue que possible tout en respectant les contraintes de fabrication du « LIGA », dans le cas préféré d'une réalisation de ce type. La géométrie est optimisée de manière à pouvoir garantir un armage calculé équivalent à environ 18°. Pour un couple plus élevé, le point extérieur de l'attache de la spire au centre peut venir certainement en contact avec le point intérieur de l'attache de la spire sur la bague (cercle roue), ce qui ne pose pas de problème et permet même de soulager partiellement les contraintes dans la spire.The geometry of the spring 67, in spiral shape, defined by the calculation is represented by the figure 10 . In order to maximize the number of winding turns of the spring, the coil must be as long as possible while respecting the manufacturing constraints of the "LIGA", in the preferred case of an embodiment of this type. The geometry is optimized so as to guarantee a calculated armature equivalent to about 18 °. For a higher torque, the outer point of the attachment of the turn in the center can certainly come in contact with the inner point of the attachment of the turn on the ring (circle wheel), which is not a problem and even allows to partially relieve the stresses in the turn.

De façon usuelle, au moins un tel mécanisme de remontage 4 du mouvement 1 est un mécanisme de remontage manuel 40 actionné par l'utilisateur. Et au moins un tel mobile d'entraînement 8 du rochet 3 selon l'invention comporte au moins une première roue d'entraînement de rochet supplémentaire 82, qui est coaxiale avec un pignon 81 attaquant le rochet 3. Cette première roue d'entraînement de rochet supplémentaire 82, porteuse d'une denture 85 agencée pour coopérer avec la denture 64 de la roue intermédiaire supplémentaire 63, est montée pivotante sur une portée 83 d'un arbre 80 que comporte le mobile d'entraînement 8 du rochet 3 . La première roue d'entraînement de rochet supplémentaire 82 est liée à cet arbre 80 par des premiers moyens de rappel élastique en rotation ou au moins un premier ressort 84 constituant des tels moyens de débrayage 9, lors du fonctionnement du mécanisme de remontage manuel 40 actionné par l'utilisateur. Une telle première roue d'entraînement de rochet supplémentaire 82 est visible en partie basse d'un mobile plus complexe illustré à la figure 11.In the usual way, at least one winding mechanism 4 of the movement 1 is a manual winding mechanism 40 actuated by the user. And at least one such driving wheel 8 of the ratchet 3 according to the invention comprises at least a first additional ratchet drive wheel 82, which is coaxial with a pinion 81 driving the ratchet 3. This first drive wheel of additional ratchet 82, carrier of a toothing 85 arranged to cooperate with the toothing 64 of the additional intermediate wheel 63, is pivotally mounted on a bearing 83 of a shaft 80 that includes the driving wheel 8 of the ratchet 3. The first additional ratchet drive wheel 82 is connected to this shaft 80 by first resiliently rotating return means or at least a first spring 84 constituting such disengaging means 9, during operation of the manual winding mechanism 40 actuated by the user. Such a first additional ratchet drive wheel 82 is visible in the lower part of a more complex mobile illustrated in FIG. figure 11 .

De façon préférée, certains de ces moyens de débrayage 9, constitués par les premiers moyens de rappel élastique en rotation ou par le au moins un premier ressort 84, exercent sur la première roue d'entraînement de rochet supplémentaire 82 un effort de friction, dont le moment du couple est différent selon le sens de pivotement relatif entre ces moyens de débrayage 9, et la première roue d'entraînement de rochet supplémentaire 82.Preferably, some of these disengaging means 9, constituted by the first resilient means of rotation in rotation or by the at least one first spring 84, exert on the first additional ratchet drive wheel 82 a frictional force, of which the moment of the torque is different according to the direction of relative pivoting between these disengaging means 9, and the first additional ratchet wheel 82.

De façon particulière, le premier ressort 84 est ainsi agencé pour générer un sens unidirectionnel de pivotement sans jeu de la première roue d'entraînement de rochet supplémentaire 82 par rapport à l'arbre 80 du mobile d'entraînement 8 du rochet 3 , de façon à prévenir toute transmission d'un couple au rouage 5 lors d'un remontage du mouvement 1 par au moins un tel mécanisme de remontage 4.In particular, the first spring 84 is thus arranged to generate a unidirectional direction of play-free pivoting of the first additional ratchet wheel 82 with respect to the shaft 80 of the driving wheel 8 of the ratchet 3, so that to prevent any transmission of a torque to the gear 5 during a reassembly of the movement 1 by at least one such winding mechanism 4.

Quand au moins un tel mécanisme de remontage 4 est un mécanisme de remontage automatique 45, au moins un tel mobile d'entraînement 8 du rochet 3 comporte encore une deuxième roue d'entraînement de rochet supplémentaire 86, tel que visible sur la figure 11. Cette deuxième roue d'entraînement de rochet supplémentaire 86, porteuse d'une denture 89 agencée pour coopérer avec le pignon 18 du mobile de réduction 16, est montée pivotante sur une portée 87 de l'arbre 80, et est liée à cet arbre 80 par des deuxièmes moyens de rappel élastique en rotation ou au moins un deuxième ressort 88 constituant des tels moyens de débrayage 9, lors du fonctionnement du mécanisme de remontage automatique 45. En somme, on dispose, d'un côté du mobile entraînement rochet 8, le système de réinjection, et de l'autre côté, le remontage automatique, ce qui explique la nécessité d'un système de débrayage entre les deux entrées de couple.When at least one such winding mechanism 4 is an automatic winding mechanism 45, at least one such driving wheel 8 of the ratchet 3 further comprises a second additional ratchet wheel 86, as visible on the figure 11 . This second additional ratchet drive wheel 86, carrier of a toothing 89 arranged to cooperate with the pinion 18 of the reduction wheel 16, is pivotally mounted on a bearing 87 of the shaft 80, and is connected to this shaft 80 by second resilient means of rotation in rotation or at least a second spring 88 constituting such means of 9, during the operation of the automatic winding mechanism 45. In short, it has, on one side of the mobile ratchet drive 8, the feedback system, and on the other side, the automatic winding, which explains the need a clutch release system between the two torque inputs.

De façon préférée, certains de ces moyens de débrayage 9, constitués par ces deuxièmes moyens de rappel élastique en rotation ou par le au moins un deuxième ressort 88, exercent sur la deuxième roue d'entraînement de rochet supplémentaire 86 un effort de friction dont le moment du couple est différent selon le sens de pivotement relatif entre les moyens de débrayage 9, et la deuxième roue d'entraînement de rochet supplémentaire 86.In a preferred manner, some of these disengaging means 9 constituted by these second elastically rotating return means or by the at least one second spring 88, exert on the second additional ratchet drive wheel 86 a friction force of which the torque moment is different in the direction of relative pivoting between the disengaging means 9, and the second additional ratchet wheel 86.

De façon particulière, le deuxième ressort 88 est ainsi agencé pour générer un sens unidirectionnel de pivotement sans jeu de la deuxième roue d'entraînement de rochet supplémentaire 86 par rapport à l'arbre 80 du mobile d'entraînement 8 du rochet 3 , de façon à prévenir toute transmission d'un couple au rouage de finissage lors d'un remontage du mouvement 1 par le mécanisme de remontage manuel 40 actionné par l'utilisateur, ou lors du fonctionnement des premiers moyens de prélèvement d'énergie 6.In particular, the second spring 88 is thus arranged to generate a unidirectional direction of play-free pivoting of the second additional ratchet drive wheel 86 with respect to the shaft 80 of the drive wheel 8 of the ratchet 3, so that to prevent any transmission of a torque to the work train during a winding movement 1 by the manual winding mechanism 40 actuated by the user, or during operation of the first energy harvesting means 6.

La conception du mobile d'entraînement 8 du rochet 3 prend ainsi en compte les différentes fonctions à remplir :

  • transmettre le couple du rouage du mécanisme de remontage automatique 45 au rochet 3 ;
  • transmettre le couple du système de réinjection ;
  • découpler la transmission des couples entre les deux systèmes, ce qui nécessite l'emploi de roues unidirectionnelles.
The design of the driving wheel 8 of ratchet 3 thus takes into account the various functions to be fulfilled:
  • transmitting the torque of the gear of the automatic winding mechanism 45 to ratchet 3;
  • transmit the torque of the feedback system;
  • decoupling torque transmission between the two systems, which requires the use of unidirectional wheels.

Il est important que, lors d'un remontage par le mécanisme de remontage automatique 45, le couple sur le mobile n'entraîne pas le système de réinjection, car, à défaut, le couple supplémentaire sur le rouage de finissage par l'intermédiaire du système de réinjection risquerait de provoquer du rebat. Dans l'autre sens, lors de l'entraînement par le système de réinjection, il faut éviter d'entraîner toutes les roues du mécanisme de remontage automatique 45 jusqu'aux roues cliquets, afin de minimiser les pertes.It is important that, during reassembly by the automatic winding mechanism 45, the torque on the mobile does not cause the feedback system, because, failing that, the additional torque on the finishing gear train via the reinjection system may cause rebat. In the other direction, during the drive by the feedback system, it is necessary to avoid driving all the wheels of the automatic winding mechanism 45 to the ratchet wheels, in order to minimize the losses.

La figure 11 montre le mobile entraînement rochet monté, composé de cinq pièces: un axe 80, de préférence décolleté en acier 20AP standard, la première roue d'entraînement de rochet supplémentaire 82 et la deuxième roue d'entraînement de rochet supplémentaire 86, qui pivotent librement, et le premier ressort 84 et le deuxième ressort 88 qui garantissent l'entraînement ou non-entraînement de ces roues.The figure 11 shows the assembled ratchet drive wheel, consisting of five parts: an axle 80, preferably a 20AP steel neck, the first additional ratchet wheel 82 and the second wheel additional ratchet drive 86, which pivot freely, and the first spring 84 and the second spring 88 which ensure the driving or non-driving of these wheels.

En ce qui concerne la première roue d'entraînement de rochet supplémentaire 82 et la deuxième roue d'entraînement de rochet supplémentaire 86 unidirectionnelles, fabriquées de préférence en Cuivre-Béryllium durci (CuBe), leur fonction est d'entraîner l'axe 80 lorsqu'elles subissent un couple en provenance, soit du mécanisme de remontage automatique 45, soit du système de réinjection. Par contre, elles ne doivent pas transmettre de couple lorsqu'elles sont entraînées par l'axe 80 (système de débrayage entre les deux roues). De plus, la roue 82 ou 86 ne doit pas avoir d'angle mort, au contraire d'une roue cliquet par exemple. De plus, les dentures 85 et 89 de ces roues 82 et 86 sont optimisées pour minimiser le jeu d'engrenage. Le comportement très différent de chaque ressort 84, 88, selon le sens du couple qui lui est appliqué peut être simplifié en un premier sens « libre » et un deuxième sens « friction » d'entraînement. Toutefois, même dans le sens dit libre du ressort, il existe un petit frottement entre le ressort et la roue concernée, du fait d'une légère précontrainte appliquée au ressort sur son diamètre extérieur, ce qui implique que la roue sera entraînée par ce faible couple de frottement, et tournera jusqu'à venir rattraper le jeu avec la roue ou le pignon suivant.With regard to the first additional ratchet drive wheel 82 and the second unidirectional supplementary ratchet wheel 86, preferably made of hardened Beryllium Copper (CuBe), their function is to drive the axis 80 when they undergo a torque from either the automatic winding mechanism 45 or the feedback system. However, they must not transmit torque when they are driven by the axis 80 (disengaging system between the two wheels). In addition, the wheel 82 or 86 must have no dead angle, unlike a ratchet wheel, for example. In addition, the teeth 85 and 89 of these wheels 82 and 86 are optimized to minimize gearing. The very different behavior of each spring 84, 88, according to the direction of the torque applied to it can be simplified in a first "free" direction and a second "friction" drive direction. However, even in the so-called free direction of the spring, there is a small friction between the spring and the wheel concerned, because of a slight preload applied to the spring on its outer diameter, which implies that the wheel will be driven by this weak friction torque, and will turn up to come catch the game with the next wheel or pinion.

Les deux roues 82 et 86 sont de préférence conçues pour recevoir le même ressort, ce qui limite le nombre de composants. De plus, leurs diamètres de pivotement sont identiques. Cela permet d'avoir la même dimension pour l'attache du ressort au centre sur l'entraînement, notamment six pans, de l'axe 80.The two wheels 82 and 86 are preferably designed to receive the same spring, which limits the number of components. In addition, their pivot diameters are identical. This allows to have the same size for the attachment of the spring in the center on the drive, including hexagon, axis 80.

Le premier 84 ou deuxième 88 ressort flexible a pour fonction d'entraîner l'axe 80 lorsqu'il travaille en sens bloquant. Dans le cas où l'axe 80 entraîne un ressort, il ne devrait pas entraîner la roue correspondante. De préférence, on minimise le couple de frottement et on maximise le couple de blocage.The first 84 or second 88 flexible spring has the function of driving the axis 80 when working in blocking direction. In the case where the axis 80 drives a spring, it should not drive the corresponding wheel. Preferably, the friction torque is minimized and the locking torque is maximized.

On comprend qu'un tel système de débrayage est indispensable pour éviter un retour de force par le rouage de réinjection, lors d'un remontage manuel ou automatique de la montre. Le mobile d'entraînement rochet 8 forme une roue unidirectionnelle dont le fonctionnement ressemble à une roue cliquet d'inversion. Le mobile 8 représente un gros progrès par rapport aux inverseurs connus, car il est beaucoup moins volumineux, et donc plus facile à implanter au voisinage immédiat du rochet 3. Le mobile 8 selon l'invention n'a pas d'angle mort, ce qui autorise son montage dans un mouvement automatique.It is understood that such a disengagement system is essential to avoid force feedback by the feedback train, during a manual or automatic winding of the watch. The ratchet drive wheel 8 forms a unidirectional wheel whose operation resembles a reversing ratchet wheel. The mobile 8 represents a big progress compared to the known inverters, because it is much less bulky, and therefore easier to implement in the vicinity Immediate ratchet 3. The mobile 8 according to the invention has no blind spot, which allows its mounting in an automatic movement.

Les figures 12 à 18 illustrent différentes géométries, non limitatives, de ressorts, qui sont applicables aussi bien au premier ressort 84 qu'au deuxième ressort 88. La figure 12 montre plus particulièrement le premier ressort 84 logé dans la première roue d'entraînement de rochet supplémentaire 82, et les figures 13 à 18 le deuxième ressort 88 logé dans la deuxième roue d'entraînement de rochet supplémentaire 86. Leur fixation à la roue correspondante est basée sur une friction: une spire externe 841, respectivement 881, du premier ressort 84, respectivement du deuxième ressort 88, coopère avec un logement 820, respectivement 860, de la roue 82, respectivement 86, dans laquelle elle est maintenue par friction au niveau de sa périphérie ou/et d'ergots 84A, respectivement 88A que comporte ledit premier ressort 84, respectivement deuxième ressort 88. La partie intérieure de chaque ressort, 842, respectivement 882, coopère avec l'arbre 80, par une partie femelle 840, respectivement 880, du premier ressort 84, respectivement du deuxième ressort 88, de profil complémentaire à une partie mâle 800 de l'arbre 80.The Figures 12 to 18 illustrate various non-limiting geometries of springs which are applicable to both the first spring 84 and the second spring 88. The figure 12 shows more particularly the first spring 84 housed in the first additional ratchet drive wheel 82, and the Figures 13 to 18 the second spring 88 housed in the second additional ratchet drive wheel 86. Their attachment to the corresponding wheel is based on a friction: an outer turn 841, respectively 881, of the first spring 84, respectively of the second spring 88, cooperates with a housing 820, respectively 860, of the wheel 82, respectively 86, in which it is held by friction at its periphery or / and lugs 84A, respectively 88A that includes said first spring 84, respectively second spring 88. The inner part of each spring, 842, respectively 882, cooperates with the shaft 80, by a female portion 840, respectively 880, of the first spring 84, respectively of the second spring 88, of complementary profile to a male portion 800 of the shaft 80.

Le profil particulier des ressorts illustrés, avec une raideur asymétrique d'au moins un bras 843, respectivement 883, joignant la partie intérieure de chaque ressort, 842, respectivement 882, à sa partie externe 841, respectivement 881, permet d'appliquer un couple avec un fort différentiel de moment, selon que le mouvement de pivotement relatif entre l'arbre 80 et la roue respective, se fait dans un sens ou dans l'autre. Le rapport du couple exercé dans un sens par rapport à l'autre est supérieur à 3 ; selon la forme du ressort, les sections utilisées, et les couples de matériaux en présence, ce rapport peut être notablement augmenté, en particulier au-delà d'un facteur 10.The particular profile of the illustrated springs, with an asymmetrical stiffness of at least one arm 843, respectively 883, joining the inner part of each spring, 842, respectively 882, to its outer portion 841, respectively 881, makes it possible to apply a torque with a strong moment differential, depending on whether the relative pivoting movement between the shaft 80 and the respective wheel, is in one direction or the other. The ratio of the torque exerted in one direction with respect to the other is greater than 3; depending on the shape of the spring, the sections used, and the pairs of materials present, this ratio can be notably increased, in particular beyond a factor of 10.

Sur les figures 12 et 13, le profil du ressort est fermé : la partie intérieure de chaque ressort, 842, respectivement 882, a la forme d'un losange centré sur l'arbre 80, une des extrémités A du losange constitue le début de la partie externe 841, respectivement 881, laquelle est circulaire selon presque un tour complet, avant de s'enrouler sur elle-même au point C et d'y former un bras 843, respectivement 883, en secteur circulaire d'environ un demi-tour, de rayon inférieur à celui de la partie externe, s'accrochant au point B à l'autre extrémité du losange symétrique à la première extrémité A.On the Figures 12 and 13 , the profile of the spring is closed: the inner part of each spring, 842, respectively 882, has the shape of a rhombus centered on the shaft 80, one of the ends A of the rhombus constitutes the beginning of the outer portion 841, respectively 881, which is circular in almost a complete turn, before winding on itself at point C and forming an arm 843, respectively 883, in a circular sector of about a half-turn, radius less than that of the outer part, clinging to point B at the other end of the symmetrical rhombus at the first end A.

Sur la figure 14, le profil du ressort est ouvert : la partie intérieure, 842, respectivement 882, a la forme d'un disque prolongé sur un rayon par un triangle, dont la pointe distale E constitue le départ d'un bras 843, respectivement 883, en secteur circulaire d'environ un demi-tour, avant de s'enrouler sur elle-même au point F et d'y former la partie externe 841, respectivement 881, laquelle est circulaire selon presque un tour complet, de rayon supérieur à celui du bras, avant de s'arrêter à une extrémité distale G.On the figure 14 , the profile of the spring is open: the inner part, 842, respectively 882, has the shape of a disk extended on a radius by a triangle, whose distal tip E is the start of an arm 843, respectively 883, in circular sector of about a half-turn, before winding on itself at the point F and forming the outer portion 841, 881 respectively, which is circular in almost a complete turn, radius greater than that of the arm, before stopping at a distal end G.

Sur la figure 15, le profil du ressort est ouvert: la partie intérieure, 842, respectivement 882, a la forme d'un disque prolongé sur un rayon par un triangle, dont la pointe distale H constitue le départ d'un bras 843, respectivement 883, en spirale croissante sur environ un demi-tour jusqu'au point I où démarre une partie externe 841, respectivement 881, circulaire, avant de s'arrêter à une extrémité distale J, après environ un tour et quart par rapport au point H.On the figure 15 , the profile of the spring is open: the inner part, 842, respectively 882, has the shape of a disk extended on a radius by a triangle, whose distal tip H constitutes the departure of an arm 843, respectively 883, in spiral increasing about half a turn to the point I where starts an outer portion 841, respectively 881, circular, before stopping at a distal end J, after about a turn and a quarter with respect to the point H.

Sur la figure 16, le profil du ressort est ouvert, le ressort comportant deux brins symétriques : la partie intérieure, 842, respectivement 882, a la forme d'un disque auquel s'accroche en K, N, un bras 843, respectivement 883, en spirale croissante sur environ trois quarts de tour jusqu'au point L, P, où démarre une partie externe 841, respectivement 881, circulaire d'un demi-tour, avant de s'arrêter à une extrémité distale M, Q.On the figure 16 , the profile of the spring is open, the spring having two symmetrical strands: the inner part, 842, respectively 882, has the shape of a disk which is hooked in K, N, an arm 843, respectively 883, spiraling increasing about three quarters of a turn to the point L, P, where starts an outer portion 841, respectively 881, circular one-half turn, before stopping at a distal end M, Q.

Sur la figure 17, le profil du ressort est fermé, et comporte un maillage avec un pas de 120° : la partie intérieure, 842, respectivement 882, a la forme d'un disque dont part au point R un bras 843, respectivement 883, sensiblement radial mais incurvé, lequel rejoint au point S une corde 885 qui joint deux secteurs circulaires de plus grand diamètre, dont un secteur TU formant une partie externe 841, respectivement 881, le ressort repartant au point U sur une autre corde 885 faisant environ 120° avec la précédente, et rejoignant au point V un autre arc incurvé radial similaire au premier, le point V étant le conjugué du point S de départ.On the figure 17 , the profile of the spring is closed, and comprises a mesh with a pitch of 120 °: the inner part, 842, respectively 882, has the shape of a disc whose part R at the point R an arm 843, respectively 883, substantially radial but curved, which joins at point S a rope 885 which joins two circular sectors of larger diameter, one sector TU forming an outer portion 841, respectively 881, the spring starting at point U on another rope 885 making about 120 ° with the previous, and joining at point V another radial arc similar to the first, the point V being the conjugate of the starting point S.

Sur la figure 18, le profil du ressort est ouvert, le ressort comportant deux brins symétriques : la partie intérieure, 842, respectivement 882, a la forme d'un disque auquel s'accroche en W un bras radial 886 de forte section, jusqu'à un point X dont part à l'équerre un bras 843, respectivement 883, de moindre section que le bras radial 886, jusqu'à une extrémité distale Y en périphérie de la roue.On the figure 18 , the profile of the spring is open, the spring having two symmetrical strands: the inner part, 842, respectively 882, has the shape of a disk which is engaged in W a radial arm 886 of strong section, up to a point X of which part at right angle arm 843, respectively 883, of less section than the radial arm 886, to a distal end Y periphery of the wheel.

Ces ressorts des figures 12 à 18 peuvent être réalisée par étampage, ou, pour ceux qui comportent des brins très fins, dans une fabrication « LIGA », « DRIE » ou similaire.These springs Figures 12 to 18 can be performed by stamping, or, for those with very fine strands, in a manufacture "LIGA", "DRIE" or similar.

Selon l'invention, le ressort principal 67 du mobile intermédiaire 60 est avantageusement dimensionné et agencé de façon à rattraper le jeu entre la roue intermédiaire supplémentaire 63 et cette roue d'entraînement de rochet supplémentaire 82.According to the invention, the main spring 67 of the intermediate wheel 60 is advantageously dimensioned and arranged to catch the clearance between the additional intermediate wheel 63 and this additional ratchet wheel 82.

Dans une variante particulière, le mouvement 1 comporte au moins un organe régulateur à balancier, et les moyens de prélèvement d'énergie 6 prélèvent un couple mécanique de façon constante sur le rouage de finissage quand cet organe régulateur fonctionne. Selon l'invention, ce balancier est dimensionné plus faiblement que ne le serait le même tel mouvement 1 dépourvu des moyens de prélèvement d'énergie 6, de façon à conserver une amplitude d'oscillation suffisante à son bon fonctionnement.In a particular variant, the movement 1 comprises at least one balance regulator member, and the energy picking means 6 take a constant mechanical torque on the work train when this regulating member is operating. According to the invention, this balance is dimensioned more weakly than would be the same such movement 1 devoid of energy harvesting means 6, so as to maintain a sufficient oscillation amplitude to its proper operation.

Dans une variante particulière, le mouvement 1 comporte au moins un organe régulateur à balancier, et au moins un tel mécanisme de remontage 4 est un mécanisme de remontage automatique 45, et les moyens de prélèvement d'énergie 6 prélèvent un couple mécanique de façon constante sur le rouage de finissage uniquement quand le mouvement 1 est maintenu dans une position fixe dans l'espace et quand le mécanisme de remontage automatique 45 est inactif, de façon à diminuer alors l'amplitude d'oscillation du balancier et à augmenter la réserve de marche du mouvement 1.In a particular variant, the movement 1 comprises at least one balance-regulating member, and at least one such winding mechanism 4 is an automatic winding mechanism 45, and the energy-taking means 6 take a constant mechanical torque. on the work train only when the movement 1 is maintained in a fixed position in space and when the automatic winding mechanism 45 is inactive, so as to then reduce the amplitude of oscillation of the balance and to increase the reserve of movement walk 1.

De préférence, dans le mouvement 1, le mécanisme de remontage 4 comporte un mécanisme de remontage manuel 40, lequel comporte une tige 41 actionnée par l'utilisateur et qui est agencée pour entraîner, dans une position axiale de remontage de la tige 41 et dans un sens de rotation de remontage qui lui est imprimé par l'utilisateur, un pignon coulant 43 agencé pour engrener avec un pignon de remontage 42 d'entraînement d'une roue couronne 44 engrenant avec le rochet 3. Selon l'invention, la roue couronne 44 est agencée pour coopérer avec un cliquet 31 comportant des moyens de rattrapage de jeu d'engrenage entre le rochet 3 et la roue couronne 44 lors d'une manoeuvre de la tige 41.Preferably, in the movement 1, the winding mechanism 4 comprises a manual winding mechanism 40, which comprises a rod 41 actuated by the user and which is arranged to drive, in an axial position of winding of the rod 41 and in a winding rotation direction which is printed to it by the user, a sliding pinion 43 arranged to mesh with a winding pinion 42 driving a crown wheel 44 meshing with the ratchet 3. According to the invention, the wheel crown 44 is arranged to cooperate with a pawl 31 comprising means of catching gear between the ratchet 3 and the crown wheel 44 during a maneuver of the rod 41.

L'invention concerne encore une pièce d'horlogerie 100, notamment une montre, comportant au moins un tel mouvement.The invention also relates to a timepiece 100, in particular a watch, comprising at least one such movement.

Le mécanisme selon l'invention doit rattraper le jeu créé dans le système de réinjection sous l'action du remontage automatique, avant de continuer d'entraîner le rochet, tout en évitant que tout le couple passe par le rouage de finissage et provoque alors du rebat. Ceci est possible quand la prise de couple sur le rouage de finissage est constante lorsque le mouvement tourne. En ce qui concerne le niveau énergétique, on diminue alors la puissance nécessaire au balancier, par la prise de couple constante de couple sur le rouage de finissage. Cela implique un redimensionnement à la baisse du balancier, pour garantir une amplitude satisfaisante. Le dimensionnement du balancier correspond directement à la diminution de couple prélevé par le système de réinjection. Dans la variante illustrée par les figures, on passe d'un mouvement de base avec un oscillateur qui possède une puissance réglante de 3100 erg/s, à un mouvement modifié qui possède une puissance réglante de 1120 erg/s. Ceci représente une diminution de l'inertie de 16mgxcm2 à 14 mgxcm2, avec corrélativement une diminution de la fréquence de 4 Hz à 3 Hz.The mechanism according to the invention must catch the game created in the reinjection system under the action of the automatic winding, before continuing to drive the ratchet, while avoiding all the torque passes through the finishing train and causes then the reshuffles. This is possible when the torque take on the finishing gear is constant when the movement is running. As regards the energy level, then decreases the power required for the balance, by the constant torque torque of the finishing gear. This implies a downsizing of the pendulum, to ensure a satisfactory amplitude. The dimensioning of the balance corresponds directly to the reduction of torque taken by the reinjection system. In the variant illustrated in the figures, we move from a basic movement with an oscillator that has a control power of 3100 erg / s, to a modified movement that has a power of 1120 erg / s. This represents a decrease of the inertia of 16mgxcm2 to 14 mgxcm2, with correlatively a decrease of the frequency from 4 Hz to 3 Hz.

Lors du porter d'une montre à mouvement automatique, le mouvement n'a pas besoin d'une augmentation de la réserve de marche. En revanche, cette autonomie devient importante au moment où l'utilisateur dépose sa montre. Dès lors, il devient intéressant d'augmenter cette réserve de marche par le système de réinjection. On peut alors, pour une montre à remontage automatique, envisager de ne pas rattraper le jeu lors du porter de la montre. Par contre, lorsque celle-ci est déposée, après un certain temps qui correspond au rattrapage de ce jeu (et qui peut être différent en fonction du porteur), une partie du couple du rouage de finissage est prélevé par le système de réinjection, qui permet d'augmenter la réserve de marche proportionnellement au couple prélevé. On conserve alors l'intégralité du couple sur le rouage de finissage lors du porter. Le balancier reste alors identique au balancier du mouvement standard (sans système de réinjection). Par contre, lors du dépôt de la montre et quand le système de réinjection se met en marche, l'amplitude du balancier va diminuer proportionnellement au couple prélevé pour la réinjection. Mais dans ce cas, la diminution d'amplitude, qui altère légèrement les performances chronométriques de la montre pendant une période de non-utilisation, permet de passer plusieurs jours sans arrêt du mouvement, ce qui serait impossible sans le système de réinjection selon l'invention.When wearing an automatic movement watch, the movement does not need an increase in the power reserve. On the other hand, this autonomy becomes important at the moment when the user deposits his watch. Therefore, it becomes interesting to increase this power reserve by the feedback system. We can then, for a self-winding watch, consider not to catch the game when wearing the watch. By cons, when it is deposited after a certain time that corresponds to the catching of this game (and which may be different depending on the carrier), a part of the torque of the work train is taken by the feedback system, which allows to increase the power reserve in proportion to the couple taken. It retains the entire torque on the gear train when wearing. The balance remains identical to the balance of the standard movement (without reinjection system). By cons, when depositing the watch and when the feedback system starts, the amplitude of the pendulum will decrease proportionally to the torque taken for reinjection. But in this case, the decrease in amplitude, which slightly alters the chronometric performance of the watch during a period of non-use, allows to spend several days without stopping the movement, which would be impossible without the reinjection system according to the invention.

Le système de rattrapage de jeu d'engrenage permet de rattraper le jeu d'engrènement provoqué lors du remontage automatique, ce qui permet d'assurer un contact permanent avec la denture du rochet même lorsqu'il est entraîné. L'utilisation d'une roue unidirectionnelle sans jeu au niveau du mobile intermédiaire 60 constitue une bonne solution: elle tourne librement dans un sens et bloque dans l'autre, le tout avec un angle mort très faible. Concernant le jeu d'engrenage, on peut encore utiliser une géométrie de denture avec un jeu réduit, ou une denture sans jeu comprenant des éléments de denture flexibles.The gear set retrofit system makes it possible to compensate for the backlash caused during automatic winding, which makes it possible to ensure permanent contact with the toothing of the ratchet even when it is driven. The use of a unidirectional wheel without play at the intermediate mobile 60 is a good solution: it turns freely in one direction and blocks in the other, all with a very low dead angle. Regarding the gear set, it is still possible to use a tooth geometry with a reduced clearance, or a no-play toothing comprising flexible teeth elements.

Le mécanisme selon l'invention répond bien aux critères suivants:

  • sécurité du système lors du fonctionnement ;
  • simplicité de réalisation et d'implémentation dans un mouvement existant ;
  • fiabilité du système à la fois pour mouvement manuel et automatique ;
  • efficacité optimale de réinjection en diminuant au maximum les pertes ;
The mechanism according to the invention satisfies the following criteria:
  • system safety during operation;
  • simplicity of realization and implementation in an existing movement;
  • system reliability for both manual and automatic movement;
  • optimal reinjection efficiency by minimizing losses;

La solution sans angles morts permet d'augmenter au maximum l'efficacité dans un mouvement à remontage automatique. Le système de débrayage par une roue unidirectionnelle répond aux impératifs de simplicité d'implémentation et de réalisation. Cela permet de limiter le nombre de composants et leur complexité.The solution without blind spots maximizes efficiency in a self-winding movement. The release system by a unidirectional wheel meets the requirements of simplicity of implementation and realization. This makes it possible to limit the number of components and their complexity.

Les fonctionnalités de rattrapage de jeu et blocage sont assurées à chaque fois directement par un composant unique.The catch-up and blocking features are each time provided directly by a single component.

Claims (15)

  1. Mechanical timepiece movement (1), including at least one energy storage means (2) fed at input by a ratchet (3) driven by at least one winding mechanism (4) and powering at output a going train, characterized in that the mechanism includes first energy take-up means (6) connected to at least one wheel set of said going train by at least a first elastic connection (7) forming an uncoupling mechanism, said first energy take-up means (6) taking up energy from said going train which is powered by said energy storage means (2), and said first energy take-up means (6) cooperating with at least one wheel set (8) driving said ratchet (3), said drive wheel set (8) is in mesh with said ratchet (3) to feed said energy storage means (2) by reinjecting part of the energy taken up by said energy take-up means (6).
  2. Movement (1) according to claim 1, characterized in that said at least one drive wheel set (8) is uncouplable under the action of at least one uncoupling mechanism (9) active during the operation of said at least one winding mechanism (4).
  3. Movement (1) according to claim 2, characterized in that said first elastic connection (7) forming the uncoupling mechanism is inserted between said energy take-up means (6) and said ratchet (3).
  4. Movement (1) according to any of claims 1 to 3, characterized in that said energy take-up means (6) are located downstream of said energy storage means (2), on at least one intermediate wheel set (60) which includes, arranged coaxially on both sides of a first pinion (61) driven by said energy storage means (2), on the one hand, an intermediate wheel (62) for connection to a wheel set of said going train, said intermediate wheel (62) pivoting integrally with said first pinion (61), and on the other hand, an additional intermediate connection wheel (63) meshing with a said wheel set (8) driving said ratchet (3), said additional intermediate wheel (63) being mounted to pivot on an arbor (68) comprised in said intermediate wheel (60) and connected to said arbor (68) by elastic rotational return means or at least a main spring (67) forming said first elastic connection (7).
  5. Movement (1) according to any of claims 1 to 4, characterized in that at least one said winding mechanism (4) is a user-actuated manual winding mechanism (40), and in that at least one said wheel set (8) driving said ratchet (3) includes at least a first additional ratchet drive wheel (82) coaxial with a pinion (81) engaging said ratchet (3), said first additional ratchet drive wheel (82) being mounted to pivot on an arbor (80) comprised in said wheel set (8) driving said ratchet (3), and connected to said arbor (80) by first elastic rotational return means or at least a first spring (84) forming said uncoupling means (9) during the operation of said user-actuated manual winding mechanism (40).
  6. Movement (1) according to claim 5, characterized in that, some of said uncoupling means (9), formed by said first elastic rotational return means or by said at least one first spring (84), exert on said first additional ratchet drive wheel (82) a friction force whose moment of torque is different according to the relative pivoting direction between said uncoupling means (9) and said first additional ratchet drive wheel (82).
  7. Movement (1) according to claim 5 or 6, characterized in that said first spring (84) is arranged to generate a unidirectional pivoting direction with no play of said first additional ratchet drive wheel (82) relative to said arbor (80) of said wheel set (8) driving said ratchet (3), so as to prevent any transmission of torque to said train during the winding of said movement (1) by at least one said winding mechanism (4).
  8. Movement (1) according to any of claims 5 to 7, characterized in that at least one said winding mechanism (4) is an automatic winding mechanism (45), and in that at least one said wheel set (8) driving said ratchet (3) further includes a second additional ratchet drive wheel (86), said second additional ratchet drive wheel (86) being mounted to pivot on said arbor (80) and connected to said arbor (80) by second elastic rotational return means or at least a second spring (88) forming some of said uncoupling means (9) during the operation of said automatic winding mechanism (45).
  9. Movement (1) according to claim 8, characterized in that some of said uncoupling means (9), formed by said second elastic rotational return means or by said at least one second spring (88), exert on second additional ratchet drive wheel (86) a friction force whose moment of torque is different according to the relative pivoting direction between said uncoupling means (9) and said second additional ratchet drive wheel (86).
  10. Movement (1) according to claim 8 or 9, characterized in that said second spring (88) is arranged to generate a unidirectional direction of pivoting with no play of said second additional ratchet drive wheel (86) relative to said arbor (80) of said wheel set (8) driving said ratchet (3), so as to prevent any transmission of torque to said train during the winding of said movement (1) by said user-actuated manual winding mechanism (40), or during the operation of said first energy take-up means (6).
  11. Movement (1) according to any of claims 5 to 10, characterized in that said main spring (67) is arranged to take up the play between said additional intermediate wheel (83) and said additional ratchet drive wheel (82).
  12. Movement (1) according to any of claims 1 to 11, characterized in that said movement (1) includes at least one regulating member having a balance, and in that said energy take up means (6) constantly take up mechanical torque from said going train when said regulating member is operating, and in that said balance is of smaller dimensions than the same movement (1) would be without said energy take up means (6), so as to maintain an oscillation amplitude sufficient for the proper operation thereof.
  13. Movement (1) according to any of claims 1 to 12, characterized in that said movement (1) includes at least one regulating member having a balance, and in that at least one said winding mechanism (4) is an automatic winding mechanism (45), and in that said energy take-up means (6) constantly take up mechanical torque from said going train only when said movement (1) is held in a fixed position in space and when said automatic winding mechanism (45) is inactive, so as to reduce the oscillation amplitude of said balance and to increase the power reserve of said movement (1).
  14. Movement (1) according to any of claims 1 to 13, characterized in that said winding mechanism (4) includes a manual winding mechanism (40), which includes a user-actuated stem (41) and which is arranged to drive, in an axial winding position of said stem (41) and in a rotational winding direction imparted thereto by the user, a sliding pinion (43) arranged to mesh with a winding pinion (42) driving a transmission wheel (44) meshing with said ratchet (3), said transmission wheel (44) being arranged to cooperate with a click (31) including means of taking up backlash between said ratchet (3) and said transmission wheel (44) upon operation of said stem (41).
  15. Timepiece (100) including at least one movement (1) according to any of claims 1 to 14.
EP13191775.9A 2013-11-06 2013-11-06 Watch with improved power reserve Active EP2871537B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP13191775.9A EP2871537B1 (en) 2013-11-06 2013-11-06 Watch with improved power reserve
US14/514,574 US9063515B2 (en) 2013-11-06 2014-10-15 Watch with improved power reserve
JP2014222322A JP5844873B2 (en) 2013-11-06 2014-10-31 Wristwatch with improved power reserve
CN201420679993.5U CN204270011U (en) 2013-11-06 2014-11-06 Movement of mechanical clock and clock and watch
CN201410638497.XA CN104635466B (en) 2013-11-06 2014-11-06 Watch with improved power reserve
HK15109565.9A HK1208917A1 (en) 2013-11-06 2015-09-29 Watch with improved power reserve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13191775.9A EP2871537B1 (en) 2013-11-06 2013-11-06 Watch with improved power reserve

Publications (2)

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EP2871537A1 EP2871537A1 (en) 2015-05-13
EP2871537B1 true EP2871537B1 (en) 2017-01-04

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EP13191775.9A Active EP2871537B1 (en) 2013-11-06 2013-11-06 Watch with improved power reserve

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US (1) US9063515B2 (en)
EP (1) EP2871537B1 (en)
JP (1) JP5844873B2 (en)
CN (2) CN104635466B (en)
HK (1) HK1208917A1 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2871537B1 (en) * 2013-11-06 2017-01-04 ETA SA Manufacture Horlogère Suisse Watch with improved power reserve
WO2017006348A1 (en) * 2015-07-08 2017-01-12 Rao Shreyas A mechanism for increasing power reserve of the mechanical watch
EP3376308B1 (en) * 2017-03-17 2019-11-13 Montres Jaquet Droz SA Winding mechanism of a timepiece
EP3418816B1 (en) * 2017-06-20 2019-10-16 Lakeview Innovation Ltd. Balance spring with lozenge section for a mechanical clockwork of a watch and method for producing said balance spring
CN108631431B (en) * 2018-05-28 2022-03-11 深圳市创益智慧制造有限公司 Solar charger baby
JP6766284B1 (en) * 2020-03-02 2020-10-07 セイコーウオッチ株式会社 Swirl springs, torque generators, watch movements and watches
EP3985454B1 (en) * 2020-10-14 2023-03-29 The Swatch Group Research and Development Ltd Winding device for an automatic watch
EP4080292B1 (en) * 2021-04-23 2023-11-08 Montres Breguet S.A. Timepiece mechanism for displaying at least a single indication of the time and timepiece comprising such a mechanism
EP4215999A1 (en) * 2022-01-24 2023-07-26 Flexous Mechanisms IP B.V. Energy harvester for a wearable and/or portable device
EP4293428A1 (en) 2022-06-14 2023-12-20 Patek Philippe SA Genève Hairspring for timepiece resonator

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR661811A (en) * 1927-10-10 1929-07-30 Spring-loaded clockwork movement, especially for watches
CH318899A (en) * 1954-07-03 1957-01-31 Nicolet Watch S A Automatic winding device for a watch mounted on a vehicle fitted with a speedometer
CH379405A (en) * 1961-11-07 1964-08-14 Bueren Watch Company S A Self-winding watch movement
US3628325A (en) * 1968-07-02 1971-12-21 Seiko Instr & Electronics Self-winding watch
CH676185B5 (en) * 1989-06-01 1991-06-28 Piguet Frederic Sa
JP2008089584A (en) * 2006-09-07 2008-04-17 Seiko Instruments Inc Mainspring winding-up mechanism of timepiece
JP4838672B2 (en) * 2006-09-08 2011-12-14 セイコーインスツル株式会社 Sweep hand clock
US7832924B2 (en) * 2007-03-27 2010-11-16 Seiko Epson Corporation Timepiece
JP2008268177A (en) * 2007-03-27 2008-11-06 Seiko Epson Corp Timepiece
JP5050756B2 (en) * 2007-09-28 2012-10-17 セイコーエプソン株式会社 Mainspring device and clock
CH700058B1 (en) * 2008-12-15 2013-09-13 Francois Durafourg Assembly including a winding ratchet attached to a barrel arbor and barrel shaft for this set.
JP5551312B2 (en) * 2010-07-19 2014-07-16 ニヴァロックス−ファー ソシエテ アノニム Oscillation mechanism with elastic pivot and movable element for energy transfer
CH704650B1 (en) * 2011-03-23 2018-06-15 Lvmh Swiss Mft Sa Mechanical watch movement comprising a deformable energy accumulator in flexion and / or torsion.
CH705079A1 (en) * 2011-06-10 2012-12-14 Haute Ecole Arc Mechanical energy source for watch movement with predefined output torque.
EP2560057B1 (en) * 2011-08-17 2014-04-02 ETA SA Manufacture Horlogère Suisse Timepiece movement with reduced height and large power reserve
EP2871537B1 (en) * 2013-11-06 2017-01-04 ETA SA Manufacture Horlogère Suisse Watch with improved power reserve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2871537A1 (en) 2015-05-13
JP5844873B2 (en) 2016-01-20
CN104635466A (en) 2015-05-20
JP2015090367A (en) 2015-05-11
US20150124572A1 (en) 2015-05-07
CN104635466B (en) 2017-04-12
HK1208917A1 (en) 2016-03-18
CN204270011U (en) 2015-04-15
US9063515B2 (en) 2015-06-23

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