EP2871537B1 - Armbanduhr mit verbesserter Gangreserve - Google Patents

Armbanduhr mit verbesserter Gangreserve 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
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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.)
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Application number
EP13191775.9A
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English (en)
French (fr)
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EP2871537A1 (de
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
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ETA SA Manufacture Horlogere Suisse
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Application filed by ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP13191775.9A priority Critical patent/EP2871537B1/de
Priority to US14/514,574 priority patent/US9063515B2/en
Priority to JP2014222322A priority patent/JP5844873B2/ja
Priority to CN201410638497.XA priority patent/CN104635466B/zh
Priority to CN201420679993.5U priority patent/CN204270011U/zh
Publication of EP2871537A1 publication Critical patent/EP2871537A1/de
Priority to HK15109565.9A priority patent/HK1208917A1/xx
Application granted granted Critical
Publication of EP2871537B1 publication Critical patent/EP2871537B1/de
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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)

Claims (15)

  1. Mechanisches Uhrwerk (1), das wenigstens ein Energiespeichermittel (2) umfasst, dessen Eingang über ein Sperrrad (3) gespeist wird, das durch wenigstens einen Aufziehmechanismus (4) angetrieben wird, und dessen Ausgang ein Räderwerk versorgt, dadurch gekennzeichnet, dass es erste Energieabgreifmittel (6) umfasst, die mit wenigstens einem beweglichen Element des Räderwerks durch wenigstens eine erste elastische Verbindung (7) verbunden sind, die einen Auskuppelmechanismus bildet, wobei die ersten Energieabgreifmittel (6) die Energie des Räderwerks abgreifen, das durch das Energiespeichermittel (2) versorgt wird, und wobei die ersten Energieabgreifmittel (6) mit wenigstens einem beweglichen Antriebselement (8) des Sperrrads (3) zusammenwirken, wobei das bewegliche Antriebselement (8) mit dem Sperrrad (3) in Eingriff steht, um das Energiespeichermittel (2) durch Wiedereinleiten eines Teils der durch die Energieabgreifmittel (6) abgegriffenen Energie zu speisen.
  2. Uhrwerk (1) nach Anspruch 1, dadurch gekennzeichnet, dass das wenigstens eine bewegliche Antriebselement (8) unter der Wirkung wenigstens eines Auskuppelmechanismus (9), der während des Betriebs des wenigstens einen Aufziehmechanismus (4) aktiv ist, auskuppelbar ist.
  3. Uhrwerk (1) nach Anspruch 2, dadurch gekennzeichnet, dass die erste elastische Verbindung (7), die einen Auskuppelmechanismus bildet, zwischen die Energieabgreifmittel (6) und das Sperrrad (3) eingesetzt ist.
  4. Uhrwerk (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Energieabgreifmittel (6) dem Energiespeichermittel (2) nachgeschaltet sind auf Höhe wenigstens eines beweglichen Zwischenelements (60), das koaxial beiderseits eines durch das Energiespeichermittel (2) angetriebenen ersten Ritzels (61) einerseits ein Zwischenrad (62) für die Verbindung mit einem beweglichen Element des Räderwerks umfasst, wobei das Zwischenrad (62) mit dem ersten Ritzel (61) drehfest verbunden ist, und andererseits ein zusätzliches Verbindungszwischenrad (63) umfasst, das mit dem beweglichen Antriebselement (8) des Sperrrads (3) in Eingriff steht, wobei das zusätzliche Zwischenrad (63) an einer Welle (68), die das bewegliche Zwischenrad (60) aufweist, drehbar montiert ist und mit der Welle (68) über elastische Drehrückstellmittel oder wenigstens eine Hauptfeder (67), die die erste elastische Verbindung (7) bilden, verbunden ist.
  5. Uhrwerk (1) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass wenigstens ein Aufziehmechanismus (4) ein von dem Anwender betätigter manueller Aufziehmechanismus (40) ist und dadurch, dass wenigstens ein bewegliches Antriebselement (8) des Sperrrads (3) wenigstens ein erstes zusätzliches Antriebssperrrad (82) koaxial zu einem mit dem Sperrrad (3) in Eingriff stehenden Ritzel (81) umfasst, wobei das erste zusätzliche Antriebssperrrad (82) auf einer Welle (80), die das bewegliche Antriebselement (8) des Sperrrads (3) aufweist, drehbar montiert ist und mit der Welle (80) durch erste elastische Drehrückstellmittel oder wenigstens eine erste Feder (84), die die Auskuppelmittel (9) bilden, während des Betriebs des durch den Anwender betätigten manuellen Aufziehmechanismus (40) verbunden ist.
  6. Uhrwerk (1) nach Anspruch 5, dadurch gekennzeichnet, dass die Auskuppelmittel (9), die durch die ersten elastischen Drehrückstellmittel oder durch die wenigstens eine erste Feder (84) gebildet sind, auf das erste zusätzliche Antriebssperrrad (82) eine Reibungskraft ausüben, deren Drehmoment je nach relativer Drehrichtung zwischen den Auskuppelmitteln (9) und dem ersten zusätzlichen Antriebssperrrad (82) unterschiedlich ist.
  7. Uhrwerk (1) nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass die erste Feder (84) dafür ausgelegt ist, eine einseitig gerichtete Drehrichtung ohne Spiel des ersten zusätzlichen Antriebssperrrads (82) in Bezug auf die Welle (80) des beweglichen Antriebselements (8) des Sperrrads (3) zu erzeugen, derart, dass jegliche Übertragung eines Drehmoments an das Räderwerk während des Aufziehens des Uhrwerks (1) durch wenigstens einen Aufziehmechanismus (4) verhindert wird.
  8. Uhrwerk (1) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass wenigstens ein Aufziehmechanismus (4) ein automatischer Aufziehmechanismus (45) ist und dadurch, dass wenigstens ein bewegliches Antriebselement (8) des Sperrrads (3) außerdem ein zweites zusätzliches Antriebssperrrad (86) umfasst, wobei das zweite zusätzliche Antriebssperrrad (86) auf der Welle (80) drehbar angeordnet ist und mit der Welle (80) durch zweite elastische Drehrückstellmittel oder wenigstens eine zweite Feder (88), die die Auskuppelmittel (9) bilden, während des Betriebs des automatischen Aufziehmechanismus (45) verbunden ist.
  9. Uhrwerk (1) nach Anspruch 8, dadurch gekennzeichnet, dass die Auskuppelmittel (9), die durch die zweiten elastischen Drehrückstellmittel oder durch wenigstens eine zweite Feder (88) gebildet sind, auf das zweite zusätzliche Antriebssperrrad (86) eine Reibungskraft ausüben, deren Drehmoment je nach relativer Drehrichtung zwischen den Auskuppelmitteln (9) und dem zweiten zusätzlichen Antriebssperrrad (86) unterschiedlich ist.
  10. Uhrwerk (1) nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass die zweite Feder (88) dafür ausgelegt ist, eine einseitig gerichtete Drehrichtung ohne Spiel des zweiten zusätzlichen Antriebssperrrads (86) in Bezug auf die Welle (80) des beweglichen Antriebselements (8) des Sperrrads (3) zu erzeugen, derart, dass jegliche Übertragung eines Drehmoments auf das Räderwerk während des Aufziehens des Uhrwerks (1) durch den durch den Anwender betätigten manuellen Aufziehmechanismus (40) oder während des Betriebs der ersten Energieabgreifmittel (6) verhindert wird.
  11. Uhrwerk (1) nach einem der Ansprüche 5 bis 10, dadurch gekennzeichnet, dass die Hauptfeder (67) in einer Weise ausgelegt ist, das Spiel zwischen dem zusätzlichen Zwischenrad (83) und dem zusätzlichen Antriebssperrrad (82) auszugleichen.
  12. Uhrwerk (1) nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass das Uhrwerk (1) wenigstens ein Regulierungsorgan mit Unruh umfasst und dadurch, dass die Energieabgreifmittel (6) ein mechanisches Drehmoment auf das Räderwerk in konstanter Weise abgreifen, wenn das Regulierungsorgan in Betrieb ist, und dadurch, dass die Unruh schwächer dimensioniert ist als es der Fall wäre, wenn das Uhrwerk (1) ohne die Energieabgreifmittel (6) ausgebildet wäre, so dass eine für ihren ordnungsgemäßen Betrieb ausreichende Oszillationsamplitude aufrecht erhalten wird.
  13. Uhrwerk (1) nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass das Uhrwerk (1) wenigstens ein Regulierungsorgan mit Unruh umfasst und dadurch, dass wenigstens ein Aufziehmechanismus (4) ein automatischer Aufziehmechanismus (45) ist und dadurch, dass die Energieabgreifmittel (6) ein mechanisches Drehmoment auf das Räderwerk auf konstante Weise lediglich dann abgreifen, wenn das Uhrwerk (1) an einer räumlich festen Position gehalten wird und wenn der automatische Aufziehmechanismus (45) inaktiv ist, so dass die Oszillationsamplitude der Unruh verringert wird und die Gangreserve des Uhrwerks (1) erhöht wird.
  14. Uhrwerk (1) nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass der Aufziehmechanismus (4) einen manuellen Aufziehmechanismus (40) umfasst, der einen durch den Anwender betätigten Stift (41) aufweist und der dafür ausgelegt ist, in einer axialen Aufziehposition des Stifts (41) und in einer Aufziehdrehrichtung, die ihm vom Anwender aufgeprägt wird, einen Kupplungstrieb (43) anzutreiben, der dafür ausgelegt ist, mit einem Aufziehritzel (42) in Eingriff zu stehen, das ein Kronrad (44) antreibt, das mit dem Sperrrad (3) in Eingriff ist, wobei das Kronrad (44) dafür ausgelegt ist, mit einem Sperrkegel (31) zusammenzuwirken, der Mittel zum Ausgleichen des Spiels bei dem Eingriff zwischen dem Sperrrad (3) und dem Kronrad (4) bei einer Betätigung des Stifts (41) aufweist.
  15. Zeitmessgerät (100), das wenigstens ein Uhrwerk (1) nach einem der Ansprüche 1 bis 14 umfasst.
EP13191775.9A 2013-11-06 2013-11-06 Armbanduhr mit verbesserter Gangreserve Active EP2871537B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP13191775.9A EP2871537B1 (de) 2013-11-06 2013-11-06 Armbanduhr mit verbesserter Gangreserve
US14/514,574 US9063515B2 (en) 2013-11-06 2014-10-15 Watch with improved power reserve
JP2014222322A JP5844873B2 (ja) 2013-11-06 2014-10-31 改良されたパワーリザーブを有する腕時計
CN201410638497.XA CN104635466B (zh) 2013-11-06 2014-11-06 具有改进的动力储存的手表
CN201420679993.5U CN204270011U (zh) 2013-11-06 2014-11-06 机械钟表机芯和钟表
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 (de) 2013-11-06 2013-11-06 Armbanduhr mit verbesserter Gangreserve

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

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EP2871537B1 (de) * 2013-11-06 2017-01-04 ETA SA Manufacture Horlogère Suisse Armbanduhr mit verbesserter Gangreserve
WO2017006348A1 (en) * 2015-07-08 2017-01-12 Rao Shreyas A mechanism for increasing power reserve of the mechanical watch
EP3376308B1 (de) * 2017-03-17 2019-11-13 Montres Jaquet Droz SA Aufziehmechanismus einer uhr
EP3418816B1 (de) 2017-06-20 2019-10-16 Lakeview Innovation Ltd. Unruhfeder mit rautenförmigem querschnitt für ein mechanisches uhrwerk einer kleinuhr sowie verfahren zur herstellung der unruhfeder
CN108631431B (zh) * 2018-05-28 2022-03-11 深圳市创益智慧制造有限公司 太阳能充电宝
JP6766284B1 (ja) * 2020-03-02 2020-10-07 セイコーウオッチ株式会社 渦巻ばね、トルク発生装置、時計用ムーブメントおよび時計
EP3985454B1 (de) * 2020-10-14 2023-03-29 The Swatch Group Research and Development Ltd Aufziehvorrichtung für automatische armbanduhr
EP4080292B1 (de) * 2021-04-23 2023-11-08 Montres Breguet S.A. Uhrwerkmechanismus zur anzeige von mindestens einer einzigen zeitanzeige und uhrwerk mit einem solchen mechanismus
EP4215999A1 (de) * 2022-01-24 2023-07-26 Flexous Mechanisms IP B.V. Energiegewinner für eine wearable- und/oder tragbare vorrichtung
EP4293428A1 (de) 2022-06-14 2023-12-20 Patek Philippe SA Genève Spirale für resonator einer uhr

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

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