EP3598241A1 - Uhrmechanismus mit konstantkraftvorrichtung - Google Patents

Uhrmechanismus mit konstantkraftvorrichtung Download PDF

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Publication number
EP3598241A1
EP3598241A1 EP18184528.0A EP18184528A EP3598241A1 EP 3598241 A1 EP3598241 A1 EP 3598241A1 EP 18184528 A EP18184528 A EP 18184528A EP 3598241 A1 EP3598241 A1 EP 3598241A1
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EP
European Patent Office
Prior art keywords
intermediate spring
clock mechanism
winding
sub
elastic
Prior art date
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Granted
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EP18184528.0A
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English (en)
French (fr)
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EP3598241B1 (de
Inventor
James Hide
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Priority to EP18184528.0A priority Critical patent/EP3598241B1/de
Publication of EP3598241A1 publication Critical patent/EP3598241A1/de
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Publication of EP3598241B1 publication Critical patent/EP3598241B1/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
    • 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 supplied by a so-called constant force device.
  • Constant force devices also called equalizers, generally include, between the motor member (barrel spring) of the watch and the escapement wheel, an intermediate spiral spring which is periodically armed by the driving member and which drives the escape wheel. Examples of such devices are the Gafner equality winder or the constant force device described in the document. EP 2166419 . These devices make it possible to transmit a force to the escapement wheel which does not depend on the degree of arming of the motor member and thus to prevent the force received by the escapement and therefore by the oscillator from decreasing as the motor organ disarms.
  • 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 monobloc energy transmission mobile comprising rectilinear elastic arms which can serve as an intermediate spring for a constant force device.
  • the force delivered to the exhaust is in fact not constant. It is the amount of energy supplied to the exhaust between two successive armatures of the intermediate spring which is constant. The force decreases between two successive armatures 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 constant force device which alleviates this drawback.
  • a timepiece mechanism comprising a motor member, an oscillator, an escapement to maintain the oscillations of the oscillator, an intermediate spring for supplying the escapement with mechanical energy, one or more gears between the driving member. and the intermediate spring and a blocking device allowing periodic reinforcement of the intermediate spring by the motor member via the gear (s), 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 return moment which does not vary by more than 10%, and in that the intermediate spring is pre-armed with 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 provides 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, of sinuous elastic arms as described in CH 709914 or straight elastic arms as described in CH 704147 , all produce an elastic return moment which varies greatly, usually linearly, depending on the winding angle. Unless you choose a very high frequency of winding (very short duration between two windings), the variation of 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 exhaust is actually substantially constant, unlike the so-called constant force devices of the prior art.
  • the Figures 1 and 2 illustrate a watch mechanism 1, forming or forming part of a watch movement, with constant force device according to the invention.
  • the timepiece mechanism 1 comprises a driving member 2, a mobile 3 driven by the driving member 2, an escapement 4 and an oscillator 5.
  • the driving member 2 is typically in the form of one or more barrel springs (a single barrel spring in the example illustrated) housed in one or more respective barrels 2a (a single barrel in the example illustrated).
  • the escapement 4 is an anchor escapement, more particularly a Swiss anchor escapement, comprising an anchor 6, an escape wheel 7 cooperating with the anchor 6 and an exhaust pinion 8 coaxial and integral with the escape wheel 7, but it could be of another type.
  • the 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 to the latter 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 winding pinion 10 could be meshed directly with the barrel 2a by adapting the gear ratio.
  • the second wheel 11 meshes with the exhaust pinion 8.
  • the connecting member 12 shown alone in the figure 3 , includes a hub 16 integral in rotation with the winding pinion 10, a serge 17 integral in rotation with the second wheel 11 and elastic arms or blades 18 uniformly distributed around the hub 16 and connecting the hub 16 to the serge 17.
  • the serge 17 is in the form of a closed circle but it could alternatively be interrupted and take the form of one or more arcs of a circle.
  • 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 tensioning (by a relative rotation of the serge 17 and of the hub 16 in one direction) and restore it by relaxing (by a relative rotation of the serge 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 clamp 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 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
  • the serge 17 of the connecting member 12 is made integral in rotation with the second wheel 11 by pins 11a carried by the second wheel 11 and engaged in openings 17a made in the serge 17.
  • the openings 17a are oblong in order to compensate for any manufacturing defects, but they could have another shape, for example round.
  • the serge 17 and the second wheel 11 could be made to rotate together by any other suitable means.
  • the link 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 to rotate 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 plaintiff which are incorporated herein by reference.
  • This locking 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 exhaust pinion 8, a rotary member for blocking 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 openings with closed outline 24, 25 which respectively receive the rotary members d 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 blocking 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 movable frame 23 could however be guided in rotation.
  • the rotary drive member 21 could be kinematically connected to the escape wheel 7 in another way than by 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 another way than by being integral in rotation with the latter, for example by means of a or more gears.
  • the operation of the clock mechanism 1 is as follows.
  • the intermediate spring 19, by disarming, drives via the serge 17 the second wheel 11 which itself drives the exhaust pinion 8 therefore the escape wheel 7.
  • the escapement wheel 7, the escapement pinion 8, the rotary drive member 21, the second wheel 11 and the serge 17 of the connecting member 12 rotate in a jerky manner at the rate of oscillations of the oscillator 5, the escapement wheel 7, the escape pinion 8 and the rotary drive member 21 rotating together clockwise from the figure 1 .
  • the exhaust 4 is only supplied with energy 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 from the torque exerted by the driving 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 one of its branches rests, which keeps the winding pinion 10 and therefore the hub 16 of the connecting member 12 stationary.
  • the intermediate spring 19 is periodically armed by the drive member 2 at times which are determined by the meeting between the rotary drive member 21 and each of the drive members 26. As soon as the rotary drive member 21 comes into contact with one of the drive elements 26, it cooperates with this to move the movable frame 23 in order to disengage the rotary blocking member 22 from the stop element 27 against which it was leaning . The whole kinematic chain going from the driving member 2 to the hub 16 of the connecting member 12 is then released and begins to turn abruptly until another branch of the rotary blocking member 22 comes press the other stop member 27. During this sudden movement (considered to be instantaneous with respect to the movement of the escapement wheel 7, the escapement pinion 8 and the rotary drive member 21), the intermediate spring 19 is armed. The intermediate spring 19 will again be armed, similarly, after the meeting between the rotary drive member 21 and the other drive member 26, then the cycle is repeated.
  • the time interval between two successive windings of the intermediate spring 19 (that is to say two successive jumps of the winding pinion 10 - hub 16 - rotary locking member 22) is typically several seconds.
  • the different gear ratios in the timepiece mechanism 1 and the number of branches of the rotary drive member 21 and of the rotary locking member 22 are chosen so that the intermediate spring 19 accumulates the same amount of time on each winding. 'energy than that delivered to the exhaust 4 between two successive windings.
  • the blocking device 20 is advantageous in particular for protecting the timepiece mechanism 1 against impact and for reducing friction, as explained in the patent applications.
  • PCT / IB2018 / 052645 and PCT / IB2018 / 052646 are advantageous in particular for protecting the timepiece mechanism 1 against impact and for reducing friction, as explained in the patent applications.
  • PCT / IB2018 / 052645 and PCT / IB2018 / 052646 it is possible to use a more conventional anchor blocking device, such as that used in the Gafner equality winder or described in the patent application.
  • EP 2166419 is a more conventional anchor blocking device, such as that used in the Gafner equality winder or described in the patent application.
  • 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 link member 12 shown in the figure 3 has, because of the shape of its elastic arms 18, a preferred direction of rotation of its serge 17 relative 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 figure 3 .
  • the intermediate spring 19 is deformed to exert a return moment M ( ⁇ ) depending on the position ⁇ of the serge 17 relative to the hub 16, tending to rotate the serge 17 relative to the hub 16 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 return it to its state of rest.
  • the intermediate spring 19 is designed, in particular by its shape, to exert, in the connecting member 12, an elastic return moment M ( ⁇ ) substantially constant over a range of angular positions [ ⁇ a , ⁇ b ] of the serge 17 relative to the hub 16 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 intermediate spring 19 is pre-armed with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ] and the gear ratios and the number branches of the rotary drive member 21 and the rotary blocking member 22 are chosen so that the winding angle ⁇ remains within 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 timepiece mechanism 1 by simple angular positioning of the second wheel 11 relative to the winding pinion 10 connected by the connecting member 12 to the second wheel 11. The closer the pre-winding value ⁇ arm chosen to the value ⁇ b, the greater the operating range of the intermediate spring 19.
  • 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 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 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 return 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 member are as follows: Outside diameter of the twill: 12 mm Hub outer diameter: 2 mm Inside diameter of the twill: 10 mm Height: 0.12mm Thickness of elastic arms: 80 ⁇ m Curvilinear length of each arm: 4.91 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 16, the inner diameter of the serge 17 and 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 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 isolated connecting member 12 thus produced as a function of the angular position ⁇ of its serge 17 relative to its hub 16.
  • the simulation carried out considers the isolated connecting member 12 made of metallic glass, more precisely Vitreloy 1b, but any suitable material can be used.
  • materials such as silicon typically coated with oxide of silicon, Nivaflex® 45/18 (alloy based on cobalt, nickel and chromium), plastic or CK101 (non-alloy structural steel) are also suitable and allow the obtaining of connecting members whose moment of elastic return is substantially constant over the same angular ranges [ ⁇ a , ⁇ b ].
  • Table 3 gives, for information only, the values ⁇ a_y% , ⁇ b_y% and ⁇ (range of angular positions at substantially constant time) associated with the connecting member 12 produced by the applicant as a function of the percentage of constancy considered there as well as the associated moments of force moments M min and M max .
  • the figure 8 shows different curves representative of a normalized moment of force M ( ⁇ ) exerted by the connecting member 12 isolated as a function of the angular position ⁇ of its serge 17 relative to its hub 16 (winding angle) for different variations of section of the elastic arms 18.
  • the highest curve, designated by A1 corresponds to elastic arms 18 of constant section and thickness 30 ⁇ m.
  • the curves located below the curve A1 correspond to elastic arms 18 whose thickness decreases linearly from the hub 16 to the clamp 17, the thickness at the point of junction with the hub 16 being 30 ⁇ m for each curve, l thickness at the junction with the twill 17 being 29 ⁇ m for the curve A2, 28 ⁇ m for the curve A3 and 27 ⁇ m for the curve A4.
  • the figure 9 shows two curves B1 and B2 representative of a standardized force moment M ( ⁇ ) exerted by the connecting member 12 isolated as a function of the angular position ⁇ of its serge 17 relative to its hub 16 (winding angle) for different cross-sectional shapes of the elastic arms 18.
  • the curve la higher, B1 corresponds to elastic arms 18 of constant section and thickness 30 ⁇ m.
  • Curve B2 corresponds to elastic arms 18 whose thickness decreases linearly from the hub 16 in the middle of the arm then increases linearly from the middle of the arm to the serge 17, the thickness at the points of junction with the hub 16 and with the serge 17 being 30 ⁇ m, the thickness in the middle of the arm being 29 ⁇ m.
  • the elastic arms 18 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 ] 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 force moment is substantially constant.
  • the simulation was carried out over its normal deformation range, before the elastic arms touch, plastically deform or break. As soon as the elastic arms touch, the elastic return moment increases suddenly 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 shape as shown in the figure 7 , based on article teaching "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 return moment.
  • the present invention can be applied to a constant force escape mechanism of the type described in the patent application CH 709914 , replacing the flexible escapement wheel of this mechanism by the connecting member 12 provided with teeth to cooperate with the anchor 6.

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  • General Physics & Mathematics (AREA)
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EP18184528.0A 2018-07-19 2018-07-19 Uhrmechanismus mit konstantkraftvorrichtung Active EP3598241B1 (de)

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EP3598241A1 true EP3598241A1 (de) 2020-01-22
EP3598241B1 EP3598241B1 (de) 2022-11-09

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114518702A (zh) * 2020-11-20 2022-05-20 蒙特雷布勒盖股份有限公司 具有力控制机构的机械机芯手表

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2166419A1 (de) 2008-09-18 2010-03-24 Agenhor SA Uhrwerk, das eine Konstantkraftvorrichtung aufweist
CH704147A2 (fr) 2010-11-18 2012-05-31 Nivarox Sa Mobile de transmission d'énergie.
EP2799938A1 (de) * 2013-04-30 2014-11-05 Audemars Piguet (Renaud et Papi) SA Mechanismus zum augenblicklichen Umspringen
CH709914A2 (fr) 2014-07-23 2016-01-29 Nivarox Sa Mécanisme d'échappement à force constante.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2166419A1 (de) 2008-09-18 2010-03-24 Agenhor SA Uhrwerk, das eine Konstantkraftvorrichtung aufweist
CH704147A2 (fr) 2010-11-18 2012-05-31 Nivarox Sa Mobile de transmission d'énergie.
EP2799938A1 (de) * 2013-04-30 2014-11-05 Audemars Piguet (Renaud et Papi) SA Mechanismus zum augenblicklichen Umspringen
CH709914A2 (fr) 2014-07-23 2016-01-29 Nivarox Sa Mécanisme d'échappement à force constante.

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 (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114518702A (zh) * 2020-11-20 2022-05-20 蒙特雷布勒盖股份有限公司 具有力控制机构的机械机芯手表
EP4002016A1 (de) * 2020-11-20 2022-05-25 Montres Breguet S.A. Armbanduhr mit mechanischem uhrwerk mit kraftsteuerungsmechanismus
JP2022082425A (ja) * 2020-11-20 2022-06-01 モントレー ブレゲ・エス アー 力制御機構を伴う機械式ムーブメントウオッチ
CN114518702B (zh) * 2020-11-20 2024-03-19 蒙特雷布勒盖股份有限公司 具有力控制机构的机械机芯手表

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