EP3037894A1 - Mechanismus und Verfahren zur Geschwindigkeitseinstellung in einem Uhrwerk - Google Patents

Mechanismus und Verfahren zur Geschwindigkeitseinstellung in einem Uhrwerk Download PDF

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Publication number
EP3037894A1
EP3037894A1 EP14199773.4A EP14199773A EP3037894A1 EP 3037894 A1 EP3037894 A1 EP 3037894A1 EP 14199773 A EP14199773 A EP 14199773A EP 3037894 A1 EP3037894 A1 EP 3037894A1
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EP
European Patent Office
Prior art keywords
anchor
oscillator
escape wheel
elastic means
energy
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14199773.4A
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English (en)
French (fr)
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EP3037894B1 (de
Inventor
Stéphane von Gunten
Quentin Gubler
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Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
Original Assignee
Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
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Application filed by Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA filed Critical Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
Priority to EP14199773.4A priority Critical patent/EP3037894B1/de
Priority to EP15168251.5A priority patent/EP3040783B1/de
Publication of EP3037894A1 publication Critical patent/EP3037894A1/de
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Publication of EP3037894B1 publication Critical patent/EP3037894B1/de
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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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels
    • 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
    • G04B15/00—Escapements
    • G04B15/10—Escapements with constant impulses for the regulating mechanism
    • 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
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency

Definitions

  • the present invention relates to the field of watchmaking and is more particularly concerned with the function that an escapement and an oscillator together perform together in a watch movement and which is to adjust an average speed at the base of the different speeds in this field. watch movement. More specifically, the invention relates to a mechanism and a method for adjusting a mean angular velocity in a watch movement.
  • a driving member provides the driving energy, which a finishing gear transmits to the wheel of an escapement interacting with a mechanical oscillator.
  • the speeds of the gears in the work train are all proportional to a rotational speed, which is the speed of rotation of the escape wheel and which is imposed by the oscillations of the mechanical oscillator. These oscillations are maintained by the energy supplied by the motor unit.
  • isochronism In the field of watchmaking, isochronism is the ability of an oscillator to oscillate at a frequency that does not vary as a function of the oscillation amplitude of this oscillator. Anisochronism refers to a deficiency of an oscillator to possess this ability. Improve isochronism and / or reduce the harmful consequences of anisochronism in movements Watchmakers are constant goals of watchmakers.
  • the invention aims at least to improve the preservation of the accuracy of a watch movement over time, for example as disarms the motor of this watch movement.
  • the intermediate device comprises elastic means arranged to store substantially entirely, by elastic deformation, said amount of energy.
  • the intermediate device is configured so that its elastic means provide each cycle substantially the same amount of energy to the oscillator.
  • the elastic means regulate at a substantially constant level the amount of energy that the oscillator receives at each of its oscillations. Because of this, the amplitude of these oscillations is substantially constant over time. It follows that the eventual anisochronism of the oscillator has little or no adverse influence on the accuracy of the count of time.
  • the mechanism defined above may incorporate one or more other advantageous characteristics, alone or in combination, in particular from those defined below.
  • the intermediate device comprises an anchor for interacting the oscillator and the escape wheel.
  • the anchor comprises two lifts which are an entry lift and an exit lift provided to be alternately engaged with an escape wheel.
  • the anchor is movable between a first position, in which the entry lift can cooperate with the escape wheel, and a second position, in which the exit lift can cooperate with the escape wheel.
  • the elastic means tend to return the anchor to the first position when this anchor is between this first position and an intermediate position of unstable equilibrium.
  • the elastic means tend to recall the anchor to the second position when the anchor is between this second position and the intermediate position of unstable equilibrium.
  • each lift comprises an active profile intended to be traversed from upstream to downstream by teeth of the escape wheel.
  • upstream and downstream refer to the direction of progression of a tooth of the escape wheel during the passage of this tooth in the vicinity of the anchor, in normal operation.
  • Each active profile has a resting surface of which at least a portion is provided to temporarily block each tooth downstream.
  • Each active profile comprises a reset ramp configured to be pushed in the opposite direction to the escape wheel by each tooth when the tooth runs down this ramp downstream. At each lift, the reset ramp is arranged upstream of the resting surface so that before stopping any of the teeth downstream, each lift is pushed by this tooth.
  • the unstable equilibrium intermediate position is a third position.
  • the anchor has a fourth position, in which the anchor is retained by any of the teeth of the escape wheel when the tooth is in abutment against the resting surface and the re-entry ramp of the entry lift .
  • the fourth position is between the first position and the intermediate position of unstable equilibrium.
  • the anchor has a fifth position, in which the anchor is by any of the teeth of the escape wheel when this tooth is in abutment against the resting surface and the rearing ramp of the exit lift.
  • the fifth position is between the second position and the intermediate position of unstable equilibrium.
  • the mechanism comprises at least two flexible support blades which support the anchor so that the anchor can switch between its first and second positions by bending the flexible support blades.
  • the elastic means comprise at least one elastically flexible return blade.
  • a solution compact can be obtained.
  • the same technology can be used to manufacture resilient means and flexible support blades.
  • the elastic means realize a compression of the flexible support blades, so as to flamber these flexible support blades except in the unstable equilibrium position.
  • the flexible support blades are prestressed in compression.
  • the mechanism comprises a device for adjusting the compression of the flexible support blades by the elastic means.
  • the flexible support blades and the resiliently flexible blade (s) return (s) form part of a piece in one piece.
  • a compact solution can be obtained. It can be at a reduced cost, the flexible support blades and the elastically flexible blade (s) can be realized in a single step. In addition, a reduction of the components to be assembled can also be obtained.
  • the single piece in question can be made of a monocrystalline material.
  • the piece in one piece defines a support frame to which the flexible support blades connect the anchor.
  • the assembly of the mechanism is facilitated to the extent that it is easier to mount a single frame than to mount two frames to each of which would be connected a single flexible support plate.
  • increased accuracy can be achieved in the geometry of the assembly, particularly when the integral part is made by means of the DRIE process or a similar process such as the LiGA process.
  • the piece in one piece is a first piece in one piece.
  • the mechanism comprises a second integral piece which is part of the anchor and which is attached and fixed on a mounting portion constituting the first piece in one piece.
  • One end of each flexible support strip is connected to this mounting portion.
  • the mechanism comprises a device for adjusting the elastic means.
  • the invention also relates to a method for adjusting an average angular speed at which an intermittent rotation of an exhaust wheel subjected to a driving torque is effected in a watch movement.
  • This method comprises a repetition of cycles in each of which the escape wheel supplies an amount of energy to an oscillator so as to maintain oscillations of this oscillator which has a frequency controlling the average speed of rotation of the escape wheel.
  • the amount of energy goes from the escape wheel to the oscillator temporarily passing into a state where this amount of energy is substantially entirely stored in elastic means, by elastic deformation of these elastic means which provide each cycle substantially the same amount of energy to the oscillator.
  • the escape wheel and the oscillator are the escape wheel and the oscillator of a mechanism as defined above, which implements the method.
  • step a) one of the teeth pushes one of the rearming ramps and moves the anchor from its first position to its fourth position.
  • step b) one of the resting surfaces stops one of the teeth.
  • the method comprises a step c) in which the rocker maneuver the anchor from its fourth position to bring the anchor to cross its intermediate position unstable equilibrium.
  • step d) the elastic means actuate the anchor from its unstable equilibrium intermediate position to its second position, whereby the anchor applies the pulse to the oscillator.
  • a mechanism 1 is more precisely a mechanism for adjusting a mean angular speed in a watch movement. It comprises an assembly frame 2, which supports an oscillator 3 and an escapement 4 interacting with each other. On the figure 1 , the balance bridge or cock has been omitted for the sake of clarity.
  • the mechanism 1 is intended to be part of a vortex.
  • the invention can be implemented also in the case where the assembly frame 2 is immobilized on a plate not shown or on a bridge also not shown in a watch movement without tourbillon.
  • the assembly frame 2 is a rigid assembly, of which a part 5, a part 6 and a support frame 7 are held together by screws 8.
  • the support frame 7 is only a portion of a part 9 .
  • a spiral spring 10 is associated with a rocker 11, which is pivotally mounted so as to be able to oscillate about a pivot axis Z 1 -Z ' 1 .
  • the spiral spring 10 has two ends, one of which is fixed while being secured to the assembly frame 2. The other end of this spiral spring 10 is a movable end which is secured to the rocker arm 11.
  • the rocker arm 11 comprises a shaft 12 for its pivotal mounting, and a flywheel 13 and a plate 14 which are mounted on the shaft 12.
  • the part 9 has several portions fulfilling different functions.
  • One of these portions constitutes the support frame 7, as has already been explained.
  • the other portions of the part 9 are two flexible support blades 20, elastic means 21 and a mounting portion 22, which the flexible support blades 20 connect to the support frame 7.
  • An anchor 23 of the exhaust 4 is reported on the mounting portion 22, to which it is fixed by means of two rivets 24.
  • the flexible support blades 20 support the anchor 23 through the mounting portion 22, so that the anchor 23 can switch in a plane perpendicular to the pivot axis Z 1 -Z ' 1 .
  • the anchor 23 and the part 9, including its resilient means 21, form an intermediate device.
  • the elastic means 21 comprise two flexible return blades 25, which are bent and symmetrical to each other.
  • the elastic means 21 are stretched elastically between the anchor 23 and two armature levers 27. They thereby exert a pull on the anchor 23.
  • a device for adjusting the intensity of this traction comprises the two levers of arming 27, whose respective angular positions are adjustable by means of two bodies not shown for the sake of clarity. Each of these two members mates with an arming lever 27, in a square hole 28 of the arming lever 27, which can thus rotate between several adjustment positions.
  • the angular positions of the arming levers 27 determine the degree of arming of the elastic means 21 and the degree of prestress in compression of the flexible blades 20.
  • the shape and the structure of the elastic means 21 and the arming levers 27 may be different from those described above and shown in FIG. figure 1 .
  • the resilient means 21 compress the flexible support blades 20 until they are flamed up. These elastic means 21 cause the anchor 23 to be bistable when the buckling of flexible support strips 20 is effective.
  • bistable anchor is an anchor having two stable positions towards each of which it is recalled elastically.
  • the anchor 23 has two positions of stable equilibrium, which are the positions S1 and S2 at the figure 2 .
  • the anchor 23 also has an intermediate position of unstable equilibrium B, which lies between the positions S1 and S2.
  • the elastic means 21 produce an elastic return of this anchor 23 to the position S1.
  • the elastic means 21 produce an elastic return of the anchor 23 to the position S2.
  • the anchor 23 is subjected to an elastic return whose direction is reversed when the anchor 23 passes its intermediate equilibrium position. unstable B.
  • an escape wheel 30 of the exhaust 4 is intended to be subjected to a unidirectional motor torque C from a motor member such as a spring not shown. This driving torque C is exerted only in one direction, in which it tends to rotate the escape wheel 30.
  • the terms "upstream”, “downstream”, “entry”, “Exit” and similar terms refer to the direction of progression of a tooth of the escape wheel 30 in the vicinity of the anchor 23.
  • the plate 14 is thus called by reference to its function and not by reference to its shape.
  • This plate 14 comprises a mounting hub 35, which carries an arm 36 for supporting an anti-tilt locking ring 37 open at a passage 38.
  • This arm 36 has a bulge 39 designed to interact with the fork 40.
  • anchor 23 fulfills the function of what is called an "ellipse” or a "plateau pin” in conventional Swiss anchor escapements.
  • the bulge 39 passes twice in the range 40, once in one direction, once in the opposite direction. At each of its passages in the range 40, the bulge 39 causes a crossing of the intermediate position of unstable equilibrium B by the anchor 23, as will be explained later.
  • the anchor 23 comprises an anti-rollover locking pin 41, which carries a finger 42 located at the same end as the fork 40.
  • the anti-rollover locking ring 37 and the Anti-rollover locking pin 41 together prevents a shock or other parasitic phenomenon from causing an untimely crossing of the unstable equilibrium intermediate position B by the anchor 23, while the bulge 39 is at a distance from the fork 40.
  • the anti-rollover locking pin 41 is integral with the finger 42. Instead, it can be attached to this finger 42. In addition, its shape may not be cylindrical.
  • the anti-rollover locking pin 41 can be worn on the symmetrical finger of the finger referenced 42, by means of a displacement of the position of the passage 38 with respect to the bulge 39.
  • the anchor 23 comprises two arms, namely an upstream arm 43 having an inlet lift 45 and a downstream arm 44 having an outlet lift 46.
  • the lifts 45 and 46 came from material with the arms 43 and 44 of the anchor 23.
  • Each of the lifts 45 and 46 comprises a rearming ramp 47 intended to be traversed downstream and then pushed by each tooth 48 of the escape wheel 30.
  • Each of the lifts 45 and 46 further comprises a stopper 49 which has the shape of a protrusion at the downstream end of a reset ramp 47 and a resting surface 50 is provided to temporarily stop each tooth 48 after it has traveled the corresponding reset ramp 47.
  • each tooth 48 of the escape wheel 30 is identical to each other.
  • Each tooth 48 is elongated radially.
  • each tooth 48 curves downstream so as to end with a spout 51 projecting both downstream and in the opposite direction to the axis of rotation Z 2 -Z ' 2 .
  • Each spout 51 terminates in a rounded tip 52 provided to slide from upstream to downstream on the active profile, a rearming ramp 47 and a resting surface 50 forming together on each of the lifts 45 and 46.
  • three and a half teeth 48 are embraced between the lifts 45 and 46.
  • the number of teeth embraced between the lifts 45 and 46 can be increased or decreased according to the needs of the construction.
  • the teeth 48 of the escape wheel 30 are twenty in number. Depending on the needs of the construction (oscillator frequency, etc.), the escape wheel 30 could also have more than twenty teeth 48 or less than twenty teeth 48.
  • the part 9, the plate 14, the anchor 23 and the escape wheel 30 are each an integral part made of a monocrystalline material including silicon-based or quartz-based.
  • a part can be manufactured by means of, for example, the "DRIE” method (acronym for “Deep Reactive Ion Etching”).
  • the "LiGA” process (acronym for “Lithography, Galvanoformung und Abformung"), which parts 9, 14, 23 and 30 can also be made of nickel or any other material achievable by galvanic growth.
  • FIGS. Figures 4a to 4h S arrows each indicate the direction of movement of the plate 14 at a given moment, while the teeth 48a and 48b are two of the teeth 48 of the escape wheel 30.
  • the phase represented is the rest.
  • the stopper 49 of the inlet lift 45 retains the tooth 48a downstream, so that the escape wheel 30 is stationary although subjected to the engine torque C.
  • the nose 51 of the tooth 48a is located at the downstream end of the resetting ramp 47 of the inlet lift 45 so that, acting against the return produced by the elastic means 21, this tooth 48a keeps the anchor 23 away the nearest stable equilibrium position, which is the S1 position. More precisely, the tooth 48a holds the anchor 23 in the position which is referenced R1 to the figure 2 and which is a momentary stopping position.
  • the bulge 39 is engaged in the fork 40 and approaches the horn 40b among the two horns 40a and 40b forming this fork 40.
  • the bulge 39 exerts on this horn 40b a thrust P1 because of the angular speed of the balance 11, which is the case at the figure 4b .
  • the passage 38 is positioned so as to be able to be borrowed by the anti-rollover locking pin 41 and thus to allow this anti-rollover locking pin 41 to pass inside the anti-rollover locking ring 37, which allows tilting of the anchor 23 to its position of unstable equilibrium B.
  • the thrust P1 tilts the anchor 23 from its position R1 to its intermediate position of unstable equilibrium B.
  • the anchor 23 then executes the movement M1 symbolized by an arrow at the figure 2 .
  • the thrust P1 continues to cause the anchor 23 to cross its intermediate unstable equilibrium position B.
  • the elastic means 21 take the relay push P1 and in turn actuate the anchor 23 to the position S2. This is what happens at the figure 4c .
  • the entry lift 45 withdraws from the trajectory of the tooth 48a. After that, the engine torque C causes a rotation of the escape wheel 30. The movement M2 continues a few times after the rotation of the escape wheel 30.
  • the rotation of the escape wheel 30 causes the tooth 48b to meet the re-arming ramp 47 of the exit lift 46, which causes the direction of progression of the anchor 23 to be reversed.
  • the reference I1 denotes the position where this inversion of the direction of progression of the anchor 23 occurs.
  • the stopper 49 of the output lift 46 retains the tooth 48b downstream, so that the escape wheel 30 is stationary although subject to the engine torque C.
  • the nose 51 of the tooth 48b is located at the downstream end of the resetting ramp 47 of the output lift 46 so that, acting against the return produced by the elastic means 21, this tooth 48b holds the anchor 23 in the position which is referenced R2 at the figure 2 and which is a momentary stopping position.
  • the anti-rollover locking ring 37 forms a barrier for the anti-rollover locking pin 41. This barrier prevents passage of the anti-rollover locking pin 41 between the inside and the outside of the locking ring anti-rollover 37, which eliminates the possibility of an accidental rollover in case of shock.
  • the movement of the balance 11 has changed direction S between the state represented at figure 4e and the state shown in the figure 4f which is the counterpart of the state illustrated in figure 4b .
  • the return to the state of the figure 4a includes a succession of steps and actions that are similar to those described above that have led to the state of the figure 4a up to the state of the figure 4e .
  • the passage 38 is positioned to allow the anti-rollover locking pin 41 to pass outside the anti-rollover locking ring 37, thereby allowing the anchor 23 to tilt to its position. unstable balance B.
  • a thrust P4 of the bulge 39 on the horn 40a of the fork 40 tilts the anchor 23 from its position R2 towards its unstable equilibrium intermediate position B.
  • the movement of the anchor 23 due to the thrust P4 is the M4 movement at the figure 2 .
  • the thrust P4 continues to cause the anchor 23 to cross its unstable equilibrium intermediate position B. After the anchor 23 has passed its unstable equilibrium position B towards its position S1, the elastic means 21 take the relay P4 thrust and in turn actuate the anchor 23 to the position S1. This is what happens at the figure 4g .
  • the state represented on the figure 4g is the counterpart of the state represented on the figure 4c .
  • the horn 40b exerts a thrust P5 on the bulge 39, so that the rocker 11 then receives one of the pulses maintaining its oscillatory movement.
  • the movement of the anchor 23 due to the actuation thereof by the elastic means 21 is referenced M5.
  • the tooth 48b comes off the exit lift 46. After that, the engine torque C causes a rotation R of the escape wheel 30.
  • the movement M5 continues after the implementation. rotation of the escape wheel 30. As can be seen at figure 2 , the movement M5 brings the anchor 23 to a position I2, where there is a reversal of the direction of progression of this anchor 23.
  • the state represented on the figure 4h is the counterpart of the state represented on the figure 4d .
  • the spout 51 of a tooth 48 slides along the reset ramp 47 of the entry lift 45.
  • this tooth 48 exerts a thrust P6 on the entry lift 45 and thus actuates the anchor 23 to position R1.
  • the movement of the anchor 23 due to the thrust P6 is the movement M6 at the figure 2 .
  • the anti-rollover locking ring 37 forms a barrier preventing passage of the anti-rollover locking pin 41 between the inside and the outside of the anti-rollover locking ring 37, eliminating the possibility of accidental spilling in case of shock.
  • each resting surface 50 is oriented so that the force then applied by the tooth 48 on the resting surface 50 can then comprise a motor component in addition to the component due to friction and that these two components compensate in the sense that their addition passes through the center of the anchor 23 and is substantially without effect on the tilting of the anchor 23.
  • the curve C1 is a graphical representation of the torque exerted by the elastic means 21 and the flexible support blades 20 on the anchor 23, as a function of the angle at which this anchor 23 is offset from its intermediate equilibrium position.
  • unstable B The X axis and the C1 curve delimit between them a surface that lines parallel to the ordinate axis can divide into several slices. Each of these slices has an area proportional to the variation that the amount of energy stored in both the elastic means 21 and the flexible support strips 20 is known to change the angular position of the anchor 23.
  • a first quantity of energy Q1 is transferred from the driving member at the origin of the torque C, to the elastic means 21.
  • a second quantity of energy Q2 passes from the oscillator 3 with the elastic means 21.
  • the first quantity of energy Q1 and the second quantity of energy Q2 pass elastic means 21 to the oscillator 3.
  • this oscillator 3 thus covers the second quantity of energy Q2 and additionally receives the first quantity of energy Q1.
  • the first quantity of energy Q1 is again transferred from the motor unit at the origin of the torque C to the elastic means 21 during the movement M3.
  • the second quantity of energy Q2 passes from the oscillator 3 to the elastic means 21.
  • the first quantity of energy Q1 and the second quantity of energy Q2 pass elastic means 21 to the oscillator 3.
  • the oscillator 3 receives substantially twice the first quantity of energy Q1.
  • the elastic means 21 store entirely or substantially entirely, by elastic deformation, this quantity of energy .
  • the oscillator 3 receives only the energy it derives from the elastic means 21.
  • the amount of energy that the elastic means 21 provide to the oscillator 3 is substantially the same at each cycle.
  • the amount of energy that the elastic means 21 provide to the oscillator 3 at each cycle is independent of the degree of arming of the motor unit, provided that the torque C at the escape wheel has allowed the tooth 48 to have been able to bring the anchor in position R1 or R2 by the thrust P3 or P6 on one of the ramps 47. It follows that the oscillations of the oscillator 3 are constant over time, although it is the same with the accuracy of the counting of the time whatever the degree of isochronism of the oscillator 3.
  • the elastic means 21 play the role of a metering energy transmitted to the oscillator 3, thanks to which it has a very stable operation.
  • the curve C2 is a graphical representation of the torque exerted by the elastic means 21 and the flexible support blades 20 on the anchor 23, as a function of the angle at which this anchor 23 is offset with respect to its position. unstable equilibrium intermediate B.
  • the curve C1 is obtained in the case where the elastic means 21 are set so that the positions S1 and S2 are offset from each other by 20 °.
  • the curve C2 is obtained in the case where the elastic means 21 are set so that the positions S1 and S2 are shifted from one another by 15 °.
  • the amount of energy transmitted to the oscillator 3 in the case corresponding to the curve C1 is different from that transmitted to the oscillator 3 in the case corresponding to the curve C2.
  • the amplitude of the oscillations of the balance 11 can be adjusted by means of an adjustment of the elastic means 21 by means of the arming levers 27.
  • the mechanism 1 has been coupled to a motor unit in a watch movement.
  • the operation of this mechanism 1 was observed as the motor unit disarmed from a maximum armature.
  • the tests were carried out with the watch movement placed in the so-called HH position (Horizontal High), in which this watch movement is horizontal and oriented so that the dial side is on the top, with regard to the direction of the Earth's gravity.
  • the results of the tests are reported on the figure 6 , where the zero time on the abscissa axis corresponds to the start time while the arming of the motor member is maximum.
  • the curve C4 is a graphical representation of the average amplitude of the oscillations of the balance 11 as a function of time, during a running time of several days without arming action of the motor member.
  • curve C3 is a graphical representation of daytime walking (in seconds per day), that is the number of seconds gained or lost each day, as a function of time, during the same operating time of several days without arming action of the motor unit. Over a period of more than six days without arming the motor unit, the diurnal step deviated no more than one second per day from its average value, which is a very good result in terms of chronometric accuracy.
  • Mechanism 1 maintains its stable operation over a long period of time, as shown by the results of the tests outlined above.
  • a mechanism for adjusting an average angular speed in a watch movement is obtained by replacing the anchor 23 with an anchor 123 in the mechanism 1.
  • the anchor 123 can replace the anchor 23 is represented alone at the figure 7 . In what follows, only that which distinguishes it from the anchor 23 is described. In addition, when a part of the anchor 123 is identical or equivalent to a referenced part of the anchor 23, it is designated by the same reference as that part of the anchor 23.
  • each rearming ramp 47 has an upstream portion 160 and a downstream portion 161 which succeed one another without having the same slope.
  • the upstream portion 160 is more difficult to push back by a tooth 48 than the downstream portion 161.
  • a tooth 48 reaches any upstream portion 160 after the engine torque C has fallen below a certain threshold, it stops before reaching the downstream portion 161 which follows this upstream portion 150. This accelerates the stop of the oscillator, so that there is no degraded operation between the stable operation of the mechanism of setting an average speed and stopping it, the degraded operation is only of short duration.
  • a mechanism for adjusting an average speed in a watch movement is obtained by replacing the anchor 23 with an anchor 223 in the mechanism 1.
  • the anchor 223 which can replace the anchor 23 is shown alone at figure 8 . In what follows, only that which distinguishes it from the anchor 23 is described. Moreover, when a part of the anchor 223 is identical or equivalent to a referenced part of the anchor 23, it is designated by the same reference as that part of the anchor 23.
  • each re-arming ramp 47 of the anchor 223 comprises a transverse rib 262, as well as an upstream portion 260 and a downstream portion 261 that this transverse rib 262 separates from one another.
  • the transverse rib 262 forms an obstacle to be crossed.
  • a tooth 48 reaches the upstream portion 260 of any rearrangement ramp 47 after the engine torque C has fallen below a certain threshold, it stops while abutting the transverse rib 262 of this ramp. resetting 47, without ever reaching the downstream portion 161 of this reset ramp 47. This accelerates the stop of the oscillator, so that there is no degraded operation between the stable operation of the adjustment mechanism of an average speed and its stopping, the degraded operation is only of short duration.
  • the figure 11 represents a single piece 300 provided for a fourth embodiment of the invention. As long as part of the part 300 is identical or equivalent to a referenced part of the mechanism 1, it is designated by the same reference as this part of the mechanism 1.
  • the anchor 23, the flexible support blades 20, the elastic means 21 and the support frame 7 are part of the same piece in one piece, which is the piece 300.
  • the resiliently flexible return blades 25 meet at a fastening portion 370 which terminates in a fastener bulge 371.
  • This fastener bulge 371 is retained in a hole 372.
  • the fastener bulge 371 is remote from the hole 372.
  • the fastener bulge 371 is pulled to the hole 372 before being inserted therein. This arms the elastic means 21.
  • the fastener made by inserting the attachment bulge 371 into the hole 372 can be obtained from various other ways, for example by means of a clip or a snap device.
  • the piece 300 in one piece can be made of a monocrystalline material, in particular based on silicon or quartz-based. Its manufacture can, for example, use the "DRIE" method. With the aid of the "LiGA” process, the part 300 can also be made of nickel or of any other material that can be produced by galvanic growth.
  • the invention is not limited to the embodiments described above.
  • it can be incorporated in the exhaust described in the Swiss patent application CH-703 333 mentioned above, in particular by means of a replacement of the lifts of this exhaust by the lifts 45 and 46.

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EP14199773.4A 2014-12-22 2014-12-22 Mechanismus und Verfahren zur Geschwindigkeitseinstellung in einem Uhrwerk Active EP3037894B1 (de)

Priority Applications (2)

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EP14199773.4A EP3037894B1 (de) 2014-12-22 2014-12-22 Mechanismus und Verfahren zur Geschwindigkeitseinstellung in einem Uhrwerk
EP15168251.5A EP3040783B1 (de) 2014-12-22 2014-12-22 Untereinheit für einen mechanismus zur einstellung der geschwindigkeit in einem uhrwerk, und ein solcher mechanismus

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EP15168251.5A Division-Into EP3040783B1 (de) 2014-12-22 2014-12-22 Untereinheit für einen mechanismus zur einstellung der geschwindigkeit in einem uhrwerk, und ein solcher mechanismus

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Cited By (5)

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Publication number Priority date Publication date Assignee Title
EP3454122B1 (de) 2017-09-11 2020-02-19 Patek Philippe SA Genève Herstellungsverfahren mithilfe der liga-technologie einer metall-mikrostruktur mit mindestens zwei stufen
EP3637196A1 (de) 2018-10-08 2020-04-15 Manufacture et fabrique de montres et chronomètres, Ulysse Nardin Le Locle S.A. Mechanischer oszillator
CN111796503A (zh) * 2019-04-03 2020-10-20 斯沃奇集团研究及开发有限公司 可自调节的钟表振荡器
US20210294269A1 (en) * 2020-03-18 2021-09-23 The Swatch Group Research And Development Ltd Mechanical horological movement provided with an escapement comprising an anchor
US20210356911A1 (en) * 2020-05-13 2021-11-18 The Swatch Group Research And Development Ltd Horological movement comprising an escapement provided with a toothed wheel and a stopper

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107708057A (zh) * 2017-11-22 2018-02-16 江苏鹏美电声器材有限公司 具有防反装功能的喇叭内磁路组装机

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FR455443A (fr) * 1912-03-15 1913-07-30 Pierre Felicia Bauhain échappement à force constante pour pendules à balancier droit ou à balancier de torsion
EP2037335A2 (de) 2007-09-13 2009-03-18 August Enzler Anker für eine Uhrenhemmung
CH703333A2 (fr) 2010-06-22 2011-12-30 Bruno Fragniere Ancre d'échappement.
US20120120774A1 (en) * 2010-11-17 2012-05-17 Hisashi Fujieda Anchor escapement and mechanical watch having the same
EP2706416A1 (de) * 2012-09-07 2014-03-12 Nivarox-FAR S.A. Flexibler Anker mit konstanter Kraft

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US3685279A (en) * 1971-07-15 1972-08-22 Ivnghans Gmbh Fa Geb Continuous switching device for the gear mechanism of an electric wrist watch
EP1122617B1 (de) 2000-02-07 2007-08-01 Audemars Piguet (Renaud et Papi) SA Verriegelungsvorrichtung für eine Uhr
CH701921B1 (fr) * 2009-10-09 2014-07-31 Télôs Watch SA Echappement à ancre et pièce d'horlogerie comportant un tel échappement.

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Publication number Priority date Publication date Assignee Title
FR455443A (fr) * 1912-03-15 1913-07-30 Pierre Felicia Bauhain échappement à force constante pour pendules à balancier droit ou à balancier de torsion
EP2037335A2 (de) 2007-09-13 2009-03-18 August Enzler Anker für eine Uhrenhemmung
CH703333A2 (fr) 2010-06-22 2011-12-30 Bruno Fragniere Ancre d'échappement.
US20120120774A1 (en) * 2010-11-17 2012-05-17 Hisashi Fujieda Anchor escapement and mechanical watch having the same
EP2706416A1 (de) * 2012-09-07 2014-03-12 Nivarox-FAR S.A. Flexibler Anker mit konstanter Kraft

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3454122B1 (de) 2017-09-11 2020-02-19 Patek Philippe SA Genève Herstellungsverfahren mithilfe der liga-technologie einer metall-mikrostruktur mit mindestens zwei stufen
EP3637196A1 (de) 2018-10-08 2020-04-15 Manufacture et fabrique de montres et chronomètres, Ulysse Nardin Le Locle S.A. Mechanischer oszillator
CN111796503A (zh) * 2019-04-03 2020-10-20 斯沃奇集团研究及开发有限公司 可自调节的钟表振荡器
US11537085B2 (en) 2019-04-03 2022-12-27 The Swatch Group Research And Development Ltd Self-adjustable horological oscillator
US20210294269A1 (en) * 2020-03-18 2021-09-23 The Swatch Group Research And Development Ltd Mechanical horological movement provided with an escapement comprising an anchor
US11927917B2 (en) * 2020-03-18 2024-03-12 The Swatch Group Research And Development Ltd Mechanical horological movement provided with an escapement comprising an anchor
US20210356911A1 (en) * 2020-05-13 2021-11-18 The Swatch Group Research And Development Ltd Horological movement comprising an escapement provided with a toothed wheel and a stopper
US11934150B2 (en) * 2020-05-13 2024-03-19 The Swatch Group Research And Development Ltd Horological movement comprising an escapement provided with a toothed wheel and a stopper

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EP3037894B1 (de) 2018-01-31
EP3040783B1 (de) 2017-07-26

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