EP3598241B1 - Uhrmechanismus mit konstantkraftvorrichtung - Google Patents

Uhrmechanismus mit konstantkraftvorrichtung Download PDF

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Publication number
EP3598241B1
EP3598241B1 EP18184528.0A EP18184528A EP3598241B1 EP 3598241 B1 EP3598241 B1 EP 3598241B1 EP 18184528 A EP18184528 A EP 18184528A EP 3598241 B1 EP3598241 B1 EP 3598241B1
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EP
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Prior art keywords
intermediate spring
timepiece mechanism
elastic
winding
escapement
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French (fr)
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EP3598241A1 (de
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James Hide
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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    • 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
    • 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
    • G04B19/00—Indicating the time by visual means
    • G04B19/02—Back-gearing arrangements between gear train and hands

Definitions

  • the present invention relates to a timepiece mechanism, in particular for a wristwatch or pocket watch, in which the escapement is powered by a so-called constant-force device.
  • Examples of such devices are Gafner's remontoire or the constant-force device described in the document EP 2166419 . These devices make it possible to transmit to the escapement wheel a force which does not depend on the degree of winding of the driving member and thus to prevent the force received by the escapement and therefore by the oscillator from decreasing as the motor organ is disarmed.
  • the intermediate spring is in the form of sinuous elastic arms which connect a pinion to a toothed serge, the pinion assembly - elastic arms - serge constituting a one-piece flexible escape wheel.
  • a one-piece energy transmission wheel set comprising rectilinear elastic arms which can be used as an intermediate spring for a constant-force device.
  • the force delivered to the escapement is not in fact constant. It is the quantity of energy supplied to the escapement between two successive windings of the intermediate spring which is constant. The force decreases between two successive windings of the intermediate spring. The regularity of the oscillations of the oscillator is certainly much improved with such devices, but it remains disturbed.
  • the present invention aims to provide a watch mechanism with a constant-force device which mitigates this drawback.
  • a watch mechanism comprising a motor member, an oscillator, an escapement to maintain the oscillations of the oscillator, an intermediate spring to supply the escapement with mechanical energy, one or more gears between the motor member and the intermediate spring and a blocking device allowing periodic winding of the intermediate spring by the motor member via the gear or gears, characterized in that the intermediate spring is a spring with non-linear behavior which produces, between a winding angle ⁇ a and a winding angle ⁇ b separated by at least 10°, an elastic restoring moment which does not vary by more than 10%, and in that the intermediate spring is pre-wound by a value ⁇ arm included in the range [ ⁇ a , ⁇ b ], the timepiece mechanism being arranged so that, during its operation, the winding angle of the intermediate spring remains in the range [ ⁇ a , ⁇ b ].
  • the present invention also proposes a timepiece, such as a wristwatch or a pocket watch, comprising this timepiece mechanism.
  • the intermediate springs of known constant-force devices whether in the form of a spiral, sinuous elastic arms as described in CH 709914 or straight elastic arms as described in CH 704147 , all produce an elastic restoring moment which varies greatly, most often linearly, with the angle of lay. Unless you choose a very high winding frequency (very short duration between two windings), the variation in the elastic return moment will be significant and the effect will be perceptible at the level of the oscillator.
  • an intermediate spring is used whose curve of the elastic return moment as a function of the winding angle is non-linear and has a plateau, the range of winding angles corresponding to this plateau being or including the operating range of the intermediate spring in the watch mechanism.
  • the force delivered to the escapement is really substantially constant, unlike so-called constant-force devices of the state of the art.
  • the figures 1 and 2 illustrate a watch mechanism 1, forming or forming part of a watch movement, with a constant-force device according to the invention.
  • the watch mechanism 1 comprises a motor member 2, a mobile 3 driven by the motor member 2, an escapement 4 and an oscillator 5.
  • the motor member 2 is typically in the form of one or more barrel springs (a single mainspring in the example shown) housed in one or more respective barrels 2a (a single barrel in the example shown).
  • the escapement 4 is a lever escapement, more particularly a Swiss lever escapement, comprising a lever 6, an escapement wheel 7 cooperating with the lever 6 and an escapement pinion 8 coaxial and secured to the escape wheel 7, but it could be of another type.
  • Oscillator 5 can be a balance-spring, as shown, or another type of oscillator such as an oscillator without pivots with flexible guidance.
  • This constant force device 9 comprises a winding pinion 10, a second wheel 11 coaxial with the winding pinion 10 but free in rotation relative thereto and a connecting member 12 functionally interposed between the winding pinion 10 and the second wheel 11 with which it is coaxial.
  • the winding pinion 10 meshes with the wheel of the mobile 3, designated by 14, while the pinion of the mobile 3, designated by 15, meshes with the barrel 2a.
  • the second wheel 11 meshes with the escapement pinion 8.
  • the connecting member 12 shown alone in picture 3 , understand a hub 16 fixed in rotation to the winding pinion 10, a rim 17 fixed in rotation to the seconds wheel 11 and elastic arms or blades 18 uniformly distributed around the hub 16 and connecting the hub 16 to the rim 17.
  • the rim 17 is in the form of a closed circle but it could alternatively be interrupted and take the form of one or more circular arcs.
  • the set of elastic arms 18 guides the serge 17 in rotation relative to the hub 16 and constitutes a so-called intermediate spring 19 capable of storing mechanical energy by stretching (by a relative rotation of the serge 17 and the hub 16 in one direction) and restore it by relaxing (by relative rotation of the rim 17 and the hub 16 in the other direction).
  • the respective ends of the elastic arms 18 joined to the hub 16 together constitute a winding end of the intermediate spring 19.
  • the respective ends of the elastic arms 18 joined to the rim 17 together constitute a torque delivery end of the intermediate spring 19.
  • the connecting member 12 is typically one-piece. It is for example made of metal, alloy, silicon, plastic, mineral glass or metallic glass. It can be produced by machining or by the LIGA technique, in particular in the case where it is made of a metal or alloy, by deep reactive ion etching called DRIE, in particular in the case where it is made of silicon, by molding, in particular in the case where it is made of plastic or metallic glass, or by laser cutting, in particular in the case where it is made of mineral glass.
  • DRIE deep reactive ion etching
  • rim 17 of connecting member 12 is secured in rotation to seconds wheel 11 by pins 11a carried by seconds wheel 11 and engaged in openings 17a made in rim 17.
  • the openings 17a are oblong in order to compensate for any manufacturing defects, but they could have another shape, for example round.
  • the rim 17 and the second wheel 11 could be made integral in rotation by any other suitable means.
  • the connecting member 12 and the second wheel 11 could even constitute a single piece having the shape of the connecting member 12 with a toothing on the periphery of the serge 17.
  • the hub 16 of the connecting member 12 and the winding pinion 10 are fixed on the same axis by driving, gluing Or other.
  • the hub 16 and the winding pinion 10 could nevertheless be made integral in rotation in another way.
  • the constant force device 9 also comprises a blocking device 20 of the type described in the patent applications PCT/IB2018/052645 and PCT/IB2018/052646 of the applicant which are incorporated herein by reference.
  • This blocking device 20 comprises a rotary drive member 21, preferably in the form of a finger as shown, coaxial and integral in rotation with the escapement wheel 7 and the escapement pinion 8, a rotary lock 22, preferably consisting of a star as shown, coaxial and integral in rotation with the winding pinion 10 and the hub 16, and a movable frame 23 having two closed contour openings 24, 25 which respectively receive the rotary members of drive 21 and locking 22.
  • Two diametrically opposed drive elements 26 formed in the wall of the opening 24 cooperate with the rotary drive member 21.
  • Two stop elements 27 formed in the wall of the opening 25 cooperate with the rotary locking member 22.
  • the movable frame 23 is guided in translation along the double arrow F by a flexible guide device 28 with which it preferably forms a single piece.
  • the mobile frame 23 could however be guided in rotation.
  • the rotary drive member 21 could be kinematically connected to the escapement wheel 7 in a way other than being integral in rotation with the latter, for example by means of one or more gears.
  • the rotary blocking member 22 could be kinematically connected to the hub 16 and to the winding pinion 10 in a way other than by being integral in rotation with these, for example by means of a or more gears.
  • the operation of the clockwork mechanism 1 is as follows.
  • escapement wheel 7, escapement pinion 8, rotary drive member 21, seconds wheel 11 and rim 17 of connecting member 12 rotate jerkily to the rhythm of the alternations of the oscillator 5, the escapement wheel 7, the escapement pinion 8 and the rotary drive member 21 rotating together in the clockwise direction of the figure 1 .
  • the escapement 4 is powered only by energy coming from the intermediate spring 19 and therefore receives a force which does not depend on the degree of winding of the driving member 2.
  • the rotary blocking member 22 which is under tension by the torque exerted by the motor member 2 via the gear train formed by the barrel 2a, the mobile 3 and the winding pinion 10 , is blocked by one of the stop elements 27 against which bears one of its branches, which keeps the winding pinion 10 and therefore the hub 16 of the connecting member 12 stationary.
  • the intermediate spring 19 is periodically charged by the drive member 2 at times which are determined by the meeting between the rotary drive member 21 and each of the drive elements 26. As soon as the rotary drive member 21 comes into contact with one of the drive elements 26, it cooperates with the latter to move the mobile frame 23 in order to disengage the rotary blocking member 22 from the stop element 27 against which it was resting . The entire kinematic chain going from the motor member 2 to the hub 16 of the connecting member 12 is then released and begins to rotate abruptly until another branch of the rotary locking member 22 comes press the other stop element 27. During this sudden movement (considered as instantaneous with respect to the movement of the escapement wheel 7, of the escapement pinion 8 and of the rotary drive member 21), the intermediate spring 19 is armed. The intermediate spring 19 will be armed again, similarly, after the meeting between the rotary drive member 21 and the other drive element 26, then the cycle repeats.
  • the time interval separating two successive windings of the intermediate spring 19 (that is to say two successive jumps of the winding pinion 10 - hub 16 - rotary blocking member 22 assembly) is typically several seconds.
  • the different gear ratios in the watch mechanism 1 and the number of branches of the rotary drive member 21 and of the rotary blocking member 22 are chosen so that the intermediate spring 19 accumulates the same quantity of energy than that delivered to the escapement 4 between two successive windings.
  • the locking device 20 is advantageous in particular for protecting the watch mechanism 1 against shocks and for reducing friction, as explained in the patent applications PCT/IB2018/052645 and PCT/IB2018/052646 .
  • a more traditional anchor locking device such as that used in Gafner's remontoire or described in the patent application EP 2166419 .
  • the elastic arms 18 which constitute the intermediate spring 19 are specially shaped to improve the constancy of the torque or elastic return moment exerted by this intermediate spring 19 and thus improve the regularity of the oscillations of the oscillator 5.
  • the isolated connecting member 12 shown in picture 3 has, due to the shape of its elastic arms 18, a privileged direction of rotation of its rim 17 with respect to its hub 16, this direction being defined as that which allows, from its state of rest, the greatest displacement relative angular of its serge 17 by relative to its hub 16. This preferred direction of rotation is clockwise at the picture 3 .
  • the intermediate spring 19 deforms to exert a restoring moment M( ⁇ ) depending on the position ⁇ of the rim 17 relative to the hub 16, tending to cause the rim 17 to pivot relative to the hub 16 in the opposite direction to the winding direction, that is to say in the opposite direction to the privileged direction of rotation, thus tending to make it return to its state of rest.
  • the intermediate spring 19 is designed, in particular by its shape, to exert, in the connecting member 12, a substantially constant elastic return moment M( ⁇ ) over a range of angular positions [ ⁇ a , ⁇ b ] of the serge 17 with respect to hub 16 by at least 10°, preferably by at least 15°, preferably by at least 20°, preferably by at least 25°.
  • “Substantially constant” moment is understood to mean a moment not varying by more than 10%, preferably 5%, more preferably 3%, typically 1.5%, it being understood that this percentage can be further reduced.
  • the intermediate spring 19 is pre-armed with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ] and the gear ratios and the number of branches of the rotary drive member 21 and of the rotary blocking member 22 are chosen so that the winding angle ⁇ remains in this range during the operation of said mechanism, so that the elastic return moment remains substantially constant.
  • the pre-winding of the intermediate spring 19 can be carried out during the assembly of the watch mechanism 1 by simple angular positioning of the second wheel 11 with respect to the winding pinion 10 connected by the connecting member 12 to the second wheel 11. The closer the pre-winding value ⁇ arm chosen is to the value ⁇ b the greater the operating range of the intermediate spring 19 may be.
  • Each winding of the intermediate spring 19 by the drive member 2 brings the winding angle ⁇ of the intermediate spring 19 to the value ⁇ arm .
  • the elastic arms 18 can be shaped by topological optimization by applying the teaching of the publication “Design of adjustable constant-force forceps for robot-assisted surgical manipulation”, Chao-Chieh Lan et al., 2011 IEEE International Conference on Robotics and Automation, Shanghai International Conference Center, May 9-13, 2011, China .
  • the topological optimization discussed in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic arms.
  • each of the elastic arms 18 of the intermediate spring 19 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the connecting member 12 to be designed as well as the constraint "( M max -M min )/((M max +M min )/2) ⁇ 0.05” sought.
  • the inequality “(M max -M min )/((M max +M min )/2) ⁇ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range [ ⁇ a_5% , ⁇ b_5% ].
  • this connecting member 12 comprising three elastic arms 18 distributed uniformly around the hub 16.
  • This connecting member 12 corresponds to that shown in the figures.
  • the dimensions of this connecting device are as follows: External diameter of the serge: 12mm Outside diameter of the hub: 2mm Inner diameter of the serge: 10mm Height: 0.12mm Thickness of the elastic arms: 80 ⁇ m Curvilinear length of each arm: 4.91mm
  • control points Q 0 , Q 1 , Q 2 , Q 3 , Q 4 , Q 5 , Q 6 were used.
  • the coordinates of these control points are shown in Table 1 below.
  • ⁇ i> ⁇ u>Table 1 Coordinates of control points Q ⁇ /u> ⁇ sub> ⁇ u>0 ⁇ /u> ⁇ /sub> ⁇ /i> ⁇ u>to ⁇ /u> ⁇ i> ⁇ u>Q ⁇ /u> ⁇ sub> ⁇ u> ⁇ u> ⁇ u>6 ⁇ /u> ⁇ /sub> ⁇ /i> ⁇ u>.
  • the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bézier curve of order 4 based on control points Q 3 to Q 6 .
  • the graph of the figure 5 reveals the geometry of the outer diameter of the hub 16, of the inner diameter of the rim 17 and of one of the elastic arms 18 of the connecting member 12 that the applicant has designed, the geometry of said arm being defined by a curve passing through the set of point coordinates defined in table 2 above. This graph is produced in an orthonormal frame.
  • the figure 6 represents the results of a simulation of the evolution of the elastic return moment of the isolated connecting member 12 thus produced as a function of the angular position ⁇ of its rim 17 with respect to its hub 16.
  • the simulation carried out considers the insulated connecting member 12 made of metallic glass, more precisely of Vitreloy 1b, but any suitable material can be used.
  • materials such as silicon typically coated with oxide silicon, Nivaflex ® 45/18 (alloy based on cobalt, nickel and chromium), plastic or CK101 (unalloyed structural steel) are also suitable and allow the production of connecting elements whose moment of elastic return is substantially constant over the same angular ranges [ ⁇ a , ⁇ b ].
  • Table 3 gives, by way of indication, the values ⁇ a_y% , ⁇ b_y% and ⁇ (range of angular positions at substantially constant moment) associated with the connecting member 12 made by the applicant as a function of the percentage of constancy considered there as well as the associated torque values M min and M max .
  • Angle range ⁇ (°) Mmin Mmax Percent constancy y (%) 13.5 30.5 17 1,310 1,331 1.6 13 31 18 1,303 1,335 2.4 12.5 31.5 19 1,294 1,339 3.4 12 32 20 1,284 1,343 4.5 10.5 33.5 23 1,242 1,360 9.1
  • the figure 8 shows different curves representative of a normalized moment of force M( ⁇ ) exerted by the insulated connecting member 12 as a function of the angular position ⁇ of its rim 17 with respect to its hub 16 (winding angle) for different variations section of the elastic arms 18.
  • the highest curve, designated by A1 corresponds to elastic arms 18 of constant section and thickness of 30 ⁇ m.
  • curves located below curve A1 correspond to elastic arms 18 whose thickness decreases linearly from hub 16 to rim 17, the thickness at the junction point with hub 16 being 30 ⁇ m for each curve, the thickness at the point of junction with the serge 17 being 29 ⁇ m for the curve A2, 28 ⁇ m for the curve A3 and 27 ⁇ m for the curve A4.
  • An improvement in consistency is observed for curves A2, A3 and A4 compared to curve A1 over a range of angles of reinforcement of length greater than 15°.
  • the figure 9 shows two curves B1 and B2 representative of a normalized moment of force M( ⁇ ) exerted by the isolated connecting member 12 as a function of the angular position ⁇ of its rim 17 with respect to its hub 16 (winding angle) for different section shapes of the elastic arms 18.
  • the curve la higher, B1 corresponds to elastic arms 18 of constant section and thickness of 30 ⁇ m.
  • Curve B2 corresponds to elastic arms 18 whose thickness decreases linearly from the hub 16 to the middle of the arm then increases linearly from the middle of the arm to the rim 17, the thickness at the junction points with the hub 16 and with the rim 17 being 30 ⁇ m, the thickness in the middle of the arm being 29 ⁇ m.
  • An improvement in consistency is observed for curve B2 compared to curve B1 over a range of angles of reinforcement of length greater than 15°.
  • the elastic arms 18 have a variable section
  • this typically varies in a strictly monotonous manner (it increases or decreases without interruption but not necessarily linearly) over at least one continuous portion of the elastic arm representing 10% , preferably 20%, preferably 30%, preferably 40%, of the (curvilinear) length of the elastic arm.
  • the variation of the section is also chosen to improve the constancy of the elastic restoring moment over the range [ ⁇ a , ⁇ b ] compared to elastic arms of the same shape as the arms 18 but of constant section.
  • the shape of the curve C1 of the intermediate spring 19 according to the invention is very different from that of the other curves C2 to C6. None of the curves C2 to C6 presents a plateau where the moment of force is substantially constant.
  • the simulation was performed over its normal deformation range, before the elastic arms touched, plastically deformed or failed. As soon as the elastic arms touch, the elastic return moment suddenly increases in absolute value, which further distances the shape of the curves C2 to C6 from that of the curve C1 of the intermediate spring 19 according to the invention.
  • the elastic arms 18 can in particular take a form as shown in figure 7 , based on the teaching of the article “Functional joint mechanisms with constant torque outputs”, Mechanism and machine theory 62 (2013) 166-181, Chia-Wen Hou et al.
  • the height, length, thickness and/or material of the elastic arms 18, or even the inclination of the elastic arms 18 relative to the hub 16 (in the plane of the connecting member 12), can also be modified to adjust the value of the substantially constant elastic restoring moment.
  • the present invention can be applied to a constant-force escapement mechanism of the type described in the patent application CH 709914 , by replacing the flexible escape wheel of this mechanism by the connecting member 12 provided with a toothing to cooperate with the anchor 6.

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Claims (13)

  1. Uhrmechanismus (1), der ein Antriebsorgan (2), einen Oszillator (5), eine Hemmung (4) zum Aufrechterhalten der Schwingungen des Oszillators (5), eine Zwischenfeder (19) zum Versorgen der Hemmung (4) mit mechanischer Energie, ein oder mehrere Getriebe (2a, 3, 10) zwischen dem Antriebsorgan (2) und der Zwischenfeder (19) und eine Blockiervorrichtung (20) umfasst, die ein periodisches Spannen der Zwischenfeder (19) durch das Antriebsorgan (2) über das oder die Getriebe (2a, 3, 10) ermöglicht, wobei die Zwischenfeder (19) mindestens einen elastischen Arm (18) umfasst, wobei der oder jeder elastische Arm (18) eine gewundene Form aufweist, dadurch gekennzeichnet, dass die Zwischenfeder (19) eine Feder mit nichtlinearem Verhalten ist, die zwischen einem Spannungswinkel θa und einem Spannungswinkel θb, die um mindestens 10° getrennt sind, ein elastisches Rückzugsmoment erzeugt, das sich um nicht mehr als 10 % verändert, und dadurch, dass die Zwischenfeder (19) mit einem Wert θarm vorgespant ist, der im Bereich [θa, θb] enthalten ist, wobei der Uhrmechanismus (1) so gestaltet ist, dass während seines Betriebs der Spannungswinkel der Zwischenfeder (19) in dem Bereich [θa, θb] bleibt.
  2. Uhrmechanismus (1) nach Anspruch 1, dadurch gekennzeichnet, dass das elastische Rückzugsmoment, das von der Zwischenfeder (19) erzeugt wird, sich über den Bereich [θa, θb] um nicht mehr als 5 %, vorzugsweise um nicht mehr als 3 %, vorzugsweise um nicht mehr als 1,5 %, verändert.
  3. Uhrmechanismus (1) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Spannungswinkel θa und θb um mindestens 15°, vorzugsweise um mindestens 20°, vorzugsweise um mindestens 25°, getrennt sind.
  4. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Zwischenfeder (19) mehrere der elastischen Arme (18) umfasst, die gleichmäßig winklig verteilt sind.
  5. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die geometrische Form des oder jedes elastischen Arms (18) eine Bezierkurve oder eine Folge von Bezierkurven ist.
  6. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der oder jeder elastische Arm (18) einen veränderlichen Querschnitt aufweist, dessen Veränderung ausgewählt ist, um die Konstanz des elastischen Rückzugsmoments in dem Bereich [θa, θb] in Bezug auf einen elastischen Arm mit der gleichen Form aber konstantem Querschnitt zu verbessern.
  7. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Zwischenfeder (19) Teil eines Teils (12) ist, das ferner eine Nabe (16) und einen Fußkreis (17) umfasst, wobei die Zwischenfeder (19) die Nabe (16) und den Fußkreis (17) verbindet.
  8. Uhrmechanismus (1) nach Anspruch 7, dadurch gekennzeichnet, dass das Teil (12) einstückig ist.
  9. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Blockiervorrichtung (20) ein bewegliches Organ (23), ein drehbares Mitnehmerorgan (21), das kinematisch mit einem Hemmungsrad (7) und mit einem Momentabgabeende der Zwischenfeder (19) verbunden ist und dazu gestaltet ist, das bewegliche Organ (23) zu verlagern, und ein drehbares Blockierorgan (22) umfasst, das kinematisch mit einem Spannungsende der Zwischenfeder (19) und mit dem Antriebsorgan (2) verbunden ist, wobei das drehbare Blockierorgan (22) durch das bewegliche Organ (23) blockiert wird und periodisch durch die Verlagerungen des beweglichen Organs (23) deblockiert wird, die von dem drehbaren Mitnehmerorgan (21) bewirkt werden.
  10. Uhrmechanismus (1) nach Anspruch 9, dadurch gekennzeichnet, dass das drehbare Mitnehmerorgan (21) drehfest mit dem Hemmungsrad (7) ist.
  11. Uhrmechanismus (1) nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass das bewegliche Organ (23) translatorisch beweglich ist.
  12. Uhrmechanismus (1) nach einem der Ansprüche 9 bis 11, dadurch gekennzeichnet, dass das bewegliche Organ (23) erste und zweite Öffnungen (24, 25) mit geschlossenem Umriss umfasst, mit deren Wand das drehbare Mitnehmerorgan (21) beziehungsweise das drehbare Blockierorgan (22) zusammenwirken.
  13. Uhr, die einen Uhrmechanismus (1) nach einem der Ansprüche 1 bis 12 umfasst.
EP18184528.0A 2018-07-19 2018-07-19 Uhrmechanismus mit konstantkraftvorrichtung Active EP3598241B1 (de)

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EP3598241B1 true EP3598241B1 (de) 2022-11-09

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4002016A1 (de) * 2020-11-20 2022-05-25 Montres Breguet S.A. Armbanduhr mit mechanischem uhrwerk mit kraftsteuerungsmechanismus

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2166419B1 (de) 2008-09-18 2013-06-26 Agenhor SA Uhrwerk, das eine Konstantkraftvorrichtung aufweist
CH704147B1 (fr) 2010-11-18 2014-02-28 Nivarox Sa Mobile de transmission d'énergie monobloc à géométrie variable.
ES2661863T3 (es) * 2013-04-30 2018-04-04 Audemars Piguet (Renaud Et Papi) Sa Mecanismo de salto instantáneo para pieza de relojería
CH709914A2 (fr) 2014-07-23 2016-01-29 Nivarox Sa Mécanisme d'échappement à force constante.

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