EP3598243A1 - Uhrmechanismus mit organ, das sich in sprüngen bewegt - Google Patents

Uhrmechanismus mit organ, das sich in sprüngen bewegt Download PDF

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Publication number
EP3598243A1
EP3598243A1 EP18184530.6A EP18184530A EP3598243A1 EP 3598243 A1 EP3598243 A1 EP 3598243A1 EP 18184530 A EP18184530 A EP 18184530A EP 3598243 A1 EP3598243 A1 EP 3598243A1
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EP
European Patent Office
Prior art keywords
actuating spring
clock mechanism
winding
hub
sub
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
EP18184530.6A
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English (en)
French (fr)
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EP3598243B1 (de
Inventor
Samuel Tanner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Priority to EP18184530.6A priority Critical patent/EP3598243B1/de
Publication of EP3598243A1 publication Critical patent/EP3598243A1/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
    • G04B19/00—Indicating the time by visual means
    • G04B19/02—Back-gearing arrangements between gear train and hands
    • 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
    • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/24306—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator combination of different shapes, e.g. bands and discs, discs and drums
    • G04B19/2432—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement

Definitions

  • the present invention relates to a timepiece mechanism with a jumping member, in particular for the instantaneous display of a time quantity such as the date.
  • Instant watch mechanisms are known in watchmaking including a snail cam against which a rocker is supported under the action of a return spring applied against the rocker.
  • the return spring is a V-shaped, U-shaped or spiral blade.
  • the rocker slides from the lower part towards the upper part of the cam, which gradually arms the return spring, then the rocker drops from said upper part to said lower part, this sudden movement, considered instantaneous, being used to actuate an indicator such as a needle associated with a scale or a disc bearing indications and cooperating with a window.
  • Patent applications CH 702137 and EP 2241944 describe such mechanisms for a minute counter.
  • the present invention aims to remedy this drawback or at least to mitigate it and proposes for this purpose a timepiece mechanism comprising a driving member, a regulating member for regulating the driving member, a jumping member, an actuating spring, a or several gears between the driving member and the actuating spring and a winding and locking device allowing continuous winding of the driving spring by the driving member via the gear (s) and periodic disarming of the spring actuation, the actuation spring causing a jump to the jumping member at each of its disarms, characterized in that the actuation 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 return moment which does not vary by more than 10%, and in that the actuating spring is pre-armed with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ], the clock mechanism being arranged so that, during its operation, the winding angle of the actuating
  • the present invention also provides a timepiece, such as a pendulum, a wristwatch or a pocket watch, comprising this timepiece mechanism.
  • a timepiece such as a pendulum, a wristwatch or a pocket watch, comprising this timepiece mechanism.
  • the figure 1 is a block diagram of a timepiece mechanism 1 according to the invention, with a jumping member, for a timepiece such as a pendulum, a wristwatch or a pocket watch.
  • Watch mechanism 1 forms or is part of a watch movement. It comprises a drive member 2, a train 3 driven by the drive member 2, a winding and locking device 4 actuated by the train 3 and a flexible wheel 5 actuated by the winding and locking device 4.
  • the drive member 2 is typically in the form of one or more barrel springs housed in one or more respective barrels.
  • the rotation of the gear train 3 and of the barrel (s) is conventionally regulated by a regulating member 6, for example with escapement and balance-spring.
  • the drive member 2, the train 3 and the regulator member 6 are conventional and will therefore not be described in more detail.
  • the winding and blocking device 4 is shown in the figure 2 . It includes a winding mobile 7, a blocking mobile 8 and a mobile frame 9.
  • a wheel 10 of the winding mobile 7 meshes with the train 3 and is driven continuously by the latter.
  • a star 11 of the armament mobile 7, coaxial and integral in rotation with the wheel 10, is located in a first opening with closed outline 12 of the mobile frame 9 and constitutes a rotary drive member cooperating with two drive elements 13 diametrically opposed formed in the wall of the opening 12.
  • a star 14 of the locking mobile 8 is located in a second opening with closed outline 15 of the mobile frame 9 and constitutes a rotary locking member cooperating with two stop elements 16 diametrically opposite formed in the wall of the opening 15.
  • This star 14 is coaxial and integral in rotation with a pinion 17 forming part of the locking mobile 8.
  • the mobile frame 9 is guided in translation along the double arrow F by a device for flexible guide 18 with which it preferably forms a single piece.
  • the movable frame 9 could however be guided in rotation.
  • the assembly 9, 11, 14 forms a blocking device of the type described in the patent applications PCT / IB2018 / 052645 and PCT / IB2018 / 052646 of the plaintiff which are incorporated herein by reference.
  • the flexible wheel 5 is shown in figures 2 and 3 . It comprises a hub 19 coaxial and integral in rotation with the armament mobile 7, a twill 20 and elastic arms or blades 21 uniformly distributed around the hub 19 and connecting the hub 19 to the twill 20.
  • the twill 20 is thus suspended from the hub 19, and guided in rotation relative to hub 19, by the elastic arms 21.
  • the latter together form an actuating spring 22 capable of storing mechanical energy by tensioning (by rotation of the hub 19 with respect to serge 20 in one direction, namely clockwise from the figure 2 or 3 ) and restore it by relaxing (by a rotation of the twill 20 relative to the hub 19 in the Same direction).
  • the respective ends of the elastic arms 21 joined to the hub 19 together constitute a winding end of the actuating spring 22.
  • the respective ends of the elastic arms 21 joined to the clamp 20 together constitute a torque delivery end of the actuating spring 22.
  • the flexible wheel 5 also comprises an external toothing 23 integral with the serge 20. This toothing 23 meshe
  • the flexible wheel 5 is preferably in one piece. It is for example made of metal, alloy, silicon (typically coated with silicon oxide), 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 known as 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
  • a display disc 24 is fixed, for example glued, to the serge 20.
  • the display disc 24 is a date display disc carrying two series of indications “1” to “31 »And the serge 20 and the display disc 24 perform together in a jumping manner, with one jump per day, one turn in two months.
  • the indications carried by the display disc 24 are successively visible through a window of a dial of the timepiece.
  • the display disc 24 could be in one piece with the flexible wheel 5.
  • the operation of the clock mechanism 1 is as follows.
  • the armament mobile 7 and with it the hub 19 rotate continuously, at a rate determined by the oscillations of the regulating member 6, clockwise from the figure 2 under the action of the driving member 2 exerted via the gear train 3. In doing so, they continuously arm the actuating spring 22. Most of the time, the locking mobile 8, which is under tension due to the torque exerted by the actuating spring 22 is blocked by one of the stop elements 16 against which one of the branches of the star 14 is supported, which keeps the serge 20 and therefore the torque delivery end of the actuating spring 22 stationary.
  • the twill 20 is released periodically at times which are determined by the meeting between the star 11 of the armament mobile 7 and each of the drive elements 13. As soon as a branch of the star 11 comes into contact with the 'one of the drive elements 13, it cooperates with the latter to move the mobile frame 9 in order to disengage the star 14 of the locking mobile 8 from the stop element 16 against which it was leaning. Under the action of the actuating spring 22, the twill 20 and the locking mobile 8 start to turn abruptly until another branch of the star 14 comes to rest on the other element of stop 16. During this sudden movement, considered instantaneous with respect to the movement of the gear train 3 and of the winding mobile 7, the indication visible through the window is replaced by the following and the actuating spring 22 partially disarms.
  • the different gear ratios in the clockwork mechanism 1 and the number of branches of each of the stars 11 and 14 are chosen so that the actuating spring 22 accumulates between two successive disarmings (two successive jumps of the twill 20) the same amount more energy than released on each disarm.
  • the clock mechanism 1 as described above and illustrated in figures 1 and 2 is an example of realization. Many variations are possible.
  • the clock mechanism 1 could be adapted to cause the display disk 24 to display a quantity other than the date, such as the month, the day of the week, the hour, the minute or the second.
  • the armament mobile 7 could be kinematically connected to the hub 19 in another way than by being integral in rotation with the latter, for example by means of one or more gears.
  • the locking mobile 8 could be kinematically connected to the serge 20 by more than one gear.
  • Another modification could consist in making the driving member 2 mesh directly with the wheel 10.
  • the winding and blocking device 4 is advantageous in particular for protecting the timepiece mechanism 1 against shocks and for reducing friction, as explained in the patent applications PCT / IB2018 / 052645 and PCT / IB2018 / 052646 .
  • the jumping member of the clock mechanism 1 could be constituted by the hub 19.
  • the hub 19 would then be coaxial and integral in rotation with the locking mobile 8 while that the pinion 17 which meshes with the toothing 23 carried by the serge 20 would be coaxial and integral in rotation with the winding mobile 7.
  • the number of branches of each of the stars 11 and 14 would be adapted accordingly.
  • Such a variant, where the actuating spring 22 is armed by the twill 20 and disarmed by the hub 19, can be used in particular to display a quantity by means of a needle integral in rotation with the hub 19.
  • the needle can, by example, be a dead second hand.
  • the elastic arms 21 which constitute the actuating spring 22 are specially shaped to improve the constancy of the torque or elastic return moment exerted by this actuating spring 22, and therefore the constancy of the torque necessary to continuously arm this actuating spring 22, and thus improve the regularity of the oscillations of the regulating member 6.
  • the behavior of the flexible wheel 5, considered in isolation, that is to say free of any interaction with the armament mobile 7 and with the locking mobile 8, is described below .
  • the figure 3 represents this insulated flexible wheel 5.
  • the insulated flexible wheel 5 shown in the figure 3 has, because of the shape of its elastic arms 21, a preferred direction of rotation of its serge 20 relative to its hub 19, this direction being defined as that which allows, from its state of rest, the greatest displacement relative angularity of its serge 20 relative to its hub 19. This preferred direction of rotation is clockwise at the figure 3 .
  • the actuating spring 22 is deformed to exert a return moment M ( ⁇ ) depending on the position ⁇ of the twill 20 relative to the hub 19, tending to rotate the twill 20 relative to the hub 19 in the direction opposite to the winding direction, that is to say in the direction opposite to the preferred direction of rotation, thus tending to cause it to return to its state of rest.
  • the actuating spring 22 is designed, in particular by its shape, to exert, in the flexible wheel 5, an elastic return moment M ( ⁇ ) substantially constant over a range of angular positions [ ⁇ a , ⁇ b ] of the serge 20 with respect to hub 19 by at least 10 °, preferably at least 15 °, preferably at least 20 °, preferably at least 25 °.
  • substantially constant moment is meant 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 actuating spring 22 is pre-armed with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ] and the gear ratios and the numbers of branches of the stars 11 and 14 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.
  • Each disarming of the actuating spring 22 brings the winding angle ⁇ to the value ⁇ arm .
  • the elastic arms 21 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 ConfIntero on Robotics and Automation, Shanghai International ConfInter Center, May 9-13, 2011, China .
  • the topological optimization discussed in the aforementioned article uses parametric polynomial curves such as the Bézier curves to determine the geometric shape of the elastic arms.
  • each of the elastic arms 21 of the actuating spring 22 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the flexible wheel 5 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 return moment of 5% over an angular range [ ⁇ a_5% , ⁇ b_5% ].
  • this flexible wheel 5 comprises three elastic arms 21 distributed uniformly around the hub 19.
  • This flexible wheel 5 corresponds to that shown in the figures.
  • the dimensions of this flexible wheel 5 are as follows: Tooth head diameter: 26.12 mm Hub outer diameter: 4 mm Inside diameter of the twill: 20 mm Height: 0.2mm Thickness of elastic arms: 90 ⁇ m Curvilinear length of each arm: 9.82 mm
  • the Bézier curve has been 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 shows the geometry of the outer diameter of the hub 19, the inner diameter of the serge 20 and one of the elastic arms 21 of the flexible wheel 5 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 made in an orthonormal coordinate system.
  • the figure 6 represents the results of a simulation of the evolution of the elastic return moment of the insulated flexible wheel 5 thus produced as a function of the angular position ⁇ of its clamp 20 relative to its hub 19.
  • the simulation carried out considers the insulated flexible wheel 5 made of silicon coated with a layer of silicon oxide 3 ⁇ m thick, but any suitable material can be used.
  • materials such as Nivaflex® 45/18 (alloy based on cobalt, nickel and chromium), CK101 (non-alloy structural steel) or other alloys, plastic, mineral glasses or metallic glasses, for example the Vitreloy 1b, are also suitable and allow flexible wheels to be obtained, the elastic return moment of which is substantially constant over the same angular ranges [ ⁇ a , ⁇ b ].
  • the angular operating range allowing the delivery of a substantially constant moment being a constant linked to the shape of the elastic arms 21, the operating angle ⁇ b must be less than the angle ⁇ lim corresponding to the limit before plasticization or rupture of the actuating spring 22. This makes it possible to define the maximum thickness that it is possible to achieve on the arms.
  • Table 3 gives, for information only, the values ⁇ a_y% , ⁇ b_y% and ⁇ (range of angular positions at substantially constant moment) associated with the flexible wheel 5 produced by the applicant as a function of the percentage of constancy y considered as well as the associated moments of force moments M min and M max .
  • the figure 7 shows different curves representative of a normalized moment of force M ( ⁇ ) exerted by the flexible wheel 5 insulated as a function of the angular position ⁇ of its clamp 20 relative to its hub 19 (winding angle) for different section variations elastic arms 21.
  • the highest curve, designated by A1 corresponds to elastic arms 21 of constant section and thickness 30 ⁇ m.
  • the curves located below the curve A1 correspond to elastic arms 21 whose thickness decreases linearly from the hub 19 to the clamp 20, the thickness at the point of junction with the hub 19 being 30 ⁇ m for each curve, l thickness at the junction with the twill 20 being 29 ⁇ m for the curve A2, 28 ⁇ m for the curve A3 and 27 ⁇ m for the curve A4.
  • the figure 8 shows two curves B1 and B2 representative of a standardized force moment M ( ⁇ ) exerted by the flexible wheel 5 isolated as a function of the angular position ⁇ of its clamp 20 relative to its hub 19 (winding angle) for different section shapes of the elastic arms 21.
  • the highest curve, B1 corresponds to elastic arms 21 of constant section and thickness 30 ⁇ m.
  • the curve B2 corresponds to elastic arms 21 whose thickness decreases linearly from the hub 19 in the middle of the arm then increases linearly from the middle of the arm to the twill 20, the thickness at the points of junction with the hub 19 and with the twill 20 being 30 ⁇ m, the thickness in the middle of the arm being 29 ⁇ m.
  • the elastic arms 21 have a variable section
  • this typically varies strictly monotonously (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 length (curvilinear) of the elastic arm.
  • the variation of the section is also chosen to improve the constancy of the elastic return moment over the range [ ⁇ a , ⁇ b ] relative to elastic arms of the same shape as the arms 21 but of constant section.
  • the elastic arms 21 can in particular take a form as described in 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 21, or even the inclination of the elastic arms 21 relative to the hub 19 (in the plane of the flexible wheel 5), can also be modified to adjust the substantially constant elastic return moment.
EP18184530.6A 2018-07-19 2018-07-19 Uhrmechanismus mit organ, das sich in sprüngen bewegt Active EP3598243B1 (de)

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EP18184530.6A EP3598243B1 (de) 2018-07-19 2018-07-19 Uhrmechanismus mit organ, das sich in sprüngen bewegt

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EP18184530.6A EP3598243B1 (de) 2018-07-19 2018-07-19 Uhrmechanismus mit organ, das sich in sprüngen bewegt

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EP3598243A1 true EP3598243A1 (de) 2020-01-22
EP3598243B1 EP3598243B1 (de) 2022-10-19

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022106433A1 (fr) 2020-11-17 2022-05-27 Patek Philippe Sa Geneve Procede de fabrication d'une lame ressort d'un organe horloger et ladite lame ressort
WO2022106434A1 (fr) 2020-11-17 2022-05-27 Patek Philippe Sa Genève Organe horloger comprenant au moins une lame ressort

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH524847A (fr) 1970-07-10 1972-02-29 Omega Brandt & Freres Sa Louis Montre-calendrier
EP2241944A2 (de) 2009-04-15 2010-10-20 Patek Philippe SA Genève Unverzögerter Zähl-Mechanismus und Kurvenscheibe für diesen Mechanismus
CH702137B1 (fr) 2007-02-05 2011-05-13 Patek Philippe Sa Geneve Dispositif d'entraînement et de réglage d'un compteur instantané et pièce d'horlogerie comportant un tel dispositif.
EP2799938A1 (de) 2013-04-30 2014-11-05 Audemars Piguet (Renaud et Papi) SA Mechanismus zum augenblicklichen Umspringen
EP2894520A2 (de) * 2010-07-19 2015-07-15 Nivarox-FAR S.A. Schwingungsmechanismus mit elastischem und beweglichen Zapfen zur Energieübertragung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH524847A (fr) 1970-07-10 1972-02-29 Omega Brandt & Freres Sa Louis Montre-calendrier
CH702137B1 (fr) 2007-02-05 2011-05-13 Patek Philippe Sa Geneve Dispositif d'entraînement et de réglage d'un compteur instantané et pièce d'horlogerie comportant un tel dispositif.
EP2241944A2 (de) 2009-04-15 2010-10-20 Patek Philippe SA Genève Unverzögerter Zähl-Mechanismus und Kurvenscheibe für diesen Mechanismus
EP2894520A2 (de) * 2010-07-19 2015-07-15 Nivarox-FAR S.A. Schwingungsmechanismus mit elastischem und beweglichen Zapfen zur Energieübertragung
EP2799938A1 (de) 2013-04-30 2014-11-05 Audemars Piguet (Renaud et Papi) SA Mechanismus zum augenblicklichen Umspringen

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
CHAO-CHIEH LAN ET AL.: "Design of adjustable constant-force forceps for robot-assisted surgical manipulation", 2011 IEEE INTERNATIONAL CONFÉRENCE ON ROBOTICS AND AUTOMATION, - 2011
CHIA-WEN HOU: "Functional joint mechanisms with constant torque outputs", MECHANISM AND MACHINE THEORY, vol. 62, 2013, pages 166 - 181, XP028970320, DOI: doi:10.1016/j.mechmachtheory.2012.12.002

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022106433A1 (fr) 2020-11-17 2022-05-27 Patek Philippe Sa Geneve Procede de fabrication d'une lame ressort d'un organe horloger et ladite lame ressort
WO2022106434A1 (fr) 2020-11-17 2022-05-27 Patek Philippe Sa Genève Organe horloger comprenant au moins une lame ressort

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