EP3907563B1 - Uhrwerkmechanismus, das ein schwenkorgan umfasst - Google Patents

Uhrwerkmechanismus, das ein schwenkorgan umfasst Download PDF

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Publication number
EP3907563B1
EP3907563B1 EP20173411.8A EP20173411A EP3907563B1 EP 3907563 B1 EP3907563 B1 EP 3907563B1 EP 20173411 A EP20173411 A EP 20173411A EP 3907563 B1 EP3907563 B1 EP 3907563B1
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EP
European Patent Office
Prior art keywords
spring
predetermined range
elastic arm
pivoting member
timepiece mechanism
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EP20173411.8A
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English (en)
French (fr)
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EP3907563A1 (de
Inventor
Frédéric Maier
Jean-Baptiste LE BRIS
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Priority to EP20173411.8A priority Critical patent/EP3907563B1/de
Publication of EP3907563A1 publication Critical patent/EP3907563A1/de
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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • 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
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
    • 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
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0823—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement
    • G04F7/0828—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement acting in the plane of the movement

Definitions

  • the present invention relates to a timepiece mechanism comprising a pivoting member mounted on a pivoting axis and subjected to the action of at least one spring arranged to work within a predetermined range of winding angles, said spring comprising at least one arm elastic having at one of its ends a first rotary element integral at least in rotation with the pivot axis of the pivoting member, said spring having zero or negative stiffness in at least part of the predetermined range.
  • Such a pivoting member is for example a finger acting on a rocker having a feeler cooperating with a snail cam of an instantaneous minute counter mechanism of a chronograph, as described in the publication WO 2020/016818 .
  • the first rotatable element of the spring is mounted on the pivot axis of the finger so that the first end of the spring is pivoted.
  • the rocker is held against the periphery of the snail cam by said spring acting on the pivot axis of the finger, this finger itself acting on the rocker. With each revolution of the cam, the rocker rises along the cam, which progressively arms the spring.
  • the pivoting member can also be the rocker itself, the first rotating element of the spring then being mounted on the axis of the rocker.
  • the spring At its second end, the spring has a base fixed to the frame of the timepiece mechanism by two pins, so that this second end of the spring is recessed.
  • This assembly makes it possible to obtain a spring having substantially zero or slightly negative stiffness in the predetermined range of angular positions that the first rotary element can assume during operation of the mechanism. This makes it possible to reduce the intensity of the force applied to the snail cam by the spring compared to a traditional spring, thus reducing the energy required to rotate the snail cam.
  • the slightly negative stiffness of the spring also allows the finger to press on the rocker with a slightly decreasing force making it possible to partially compensate for the variation of the lever arm of the force applied to the cam by the rocker on one rotation revolution of this cam. . This makes it possible to have a lower variation in the torque required to rotate said cam.
  • the present invention aims to remedy these drawbacks by proposing a watch mechanism comprising a pivoting member subjected to the action of a spring having zero or negative stiffness, said spring being simple to mount.
  • the present invention also proposes a timepiece mechanism comprising a pivoting member subjected to the action of a spring having a negative stiffness, said spring also being simple to manufacture.
  • the present invention relates to a watch mechanism comprising a pivoting member mounted on a pivot axis and subjected to the action of at least one spring arranged to work within a predetermined range of winding angles, said spring comprising at least one elastic arm having at one of its ends a first integral rotary element at least in rotation of the pivot axis of the pivoting member, said spring having zero or negative stiffness in at least part of the predetermined range.
  • the elastic arm has at the other of its ends a second rotary element also pivotally mounted.
  • the spring can be easily put in place by the watchmaker.
  • the two pivoted ends of the spring make it possible to reduce the torque applied by the spring as well as the stress in the elastic arm with respect to a spring at one pivoted end and at the other recessed end.
  • the or each elastic arm is sinuous in shape.
  • the geometric shape of the or each elastic arm is a Bézier curve or a succession of Bézier curves.
  • the center distance between the first and second rotary elements can be chosen so that the spring has a negative or zero stiffness in said at least part of the predetermined range, preferably in substantially the entire predetermined range.
  • the or each elastic arm of the spring has a constant section, the stiffness of the spring being negative or zero in said at least part of the predetermined range, preferably in substantially the entire predetermined range.
  • the invention makes it possible in particular to obtain a spring with negative stiffness without having to change the section of the elastic arm, so that said spring is simple to manufacture.
  • the or each elastic arm of the spring has a variable section, the variation of which is chosen to make the stiffness of the spring less negative, or even zero, in said at least part of the predetermined range, preferably in substantially the whole beach predetermined, with respect to an elastic arm of the same shape but of constant section.
  • the invention makes it possible to obtain a spring whose stiffness is chosen to be zero or negative depending on the intended application for the pivoting member.
  • the invention further proposes a timepiece, such as a wristwatch or a pocket watch, comprising this timepiece mechanism.
  • stiffness means tangential stiffness
  • the present invention relates to a timepiece mechanism comprising a pivoting member mounted on a pivot axis and subjected to the action of at least one spring 100 arranged to work within a predetermined range of winding angles.
  • Said spring 100 is specially shaped to have zero or negative stiffness in at least part of the predetermined range.
  • Such a spring 100 makes it possible at least to improve, or even guarantee, the constancy of the torque or moment of force that it exerts on the pivoting member and thus at least reduce the energy consumption.
  • the spring 100 comprises at least one elastic arm 102 in the form of a blade having at one of its ends a first rotary element 104 secured at least in rotation to the pivot axis of the pivoting member.
  • Said pivot axis of the pivoting member is mounted pivoted on an element of the frame of the watch mechanism.
  • the first rotary element 104 has for example the shape of a triangular ring as on the figure 1 and 2 or circular. It is made integral in rotation with the pivot axis of the pivoting member, for example by driving on said axis or any other suitable fixing means.
  • the elastic arm 102 has at the other of its ends a second rotary element 106 also pivotally mounted.
  • the two ends of the spring 100 are advantageously pivoted.
  • the second rotating element 106 of the spring 100 is pivotally mounted on an element of the frame of the timepiece mechanism. It can be pivotally mounted, for example on a pin secured to said frame or by any other suitable mounting means.
  • the second rotary element 106 of the spring 100 is pivotally mounted on a movable element of the pivoting member arranged to be movable relative to the pivot axis of said pivoting member. It can be pivotally mounted, for example on a pin or a tenon secured to said movable element of the pivoting member or by any other suitable mounting means.
  • the second rotary element 106 has for example the shape of a circular ring as shown in the figure 1 or triangular as shown in the picture 2 .
  • the spring 100 could comprise several elastic arms connecting the two rotating elements 104, 106, depending on the intensity of the force desired product.
  • a spring comprising a single elastic arm has the advantage of greater compactness, which may be advantageous depending on the application.
  • the spring 100 is here considered as a whole as a part comprising the two rotating elements 104 and 106 connected by the elastic arm 102.
  • the two rotating elements 104 and 106 are intended to rotate on themselves, only the elastic arm 102 deforming during operation of the mechanism.
  • the first rotating element 104 can form a single piece with its pivoting member.
  • Spring 100 is preferably 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
  • the spring 100 Due to the specific shape of its elastic arm 102, the spring 100 has a privileged direction of rotation of its rotary elements 104, 106 with respect to their rest position, this direction being defined as that which allows, from a rest state of the isolated spring 100 in which its elastic arm 102 is at rest, the greatest relative angular displacement of the rotary elements 104 and 106 with respect to their rest position.
  • This privileged direction of rotation is the clockwise direction for the first rotary element 104 of the picture 2 and counterclockwise for the second rotating element 106 of the picture 2 , wherein the first rotating element 104 in white is in its rest position, and the first rotating element in black is in a constrained state after one clockwise rotation.
  • the two rotary elements 104 and 106 pivot in the opposite direction but with different angles, which vary in particular according to the center distance E between the first element 104 and the second rotary element 106, i.e. the distance between the centers of rotation of said rotary elements 104, 106.
  • ⁇ is called the angular position of the first rotating element 104 of the isolated spring 100 in a constrained state with respect to its rest position, ⁇ being equal to zero when the isolated spring 100 is at rest, that is to say when its elastic arm 102 is at rest, and increases with the angular displacement of the first rotary element 104, when the spring 100 is constrained, relative to its rest position in the preferred direction of rotation of said first rotary element 104.
  • the spring 100 is said to be armed with x.
  • the spring 100 differs from conventional elastic structures. Its properties are based on a sinuous shape of its elastic arm 102 which deforms so as to generate, in particular when its section is constant, a moment which decreases over a predetermined range of angular positions of its first rotary element 104 with respect to its position of rotation. rest, the spring 100 then having a negative stiffness over said range, or a substantially constant moment over a predetermined range of angular positions of its first rotary element 104 with respect to its rest position, the spring 100 then having a substantially zero stiffness over said range, when the two ends of the spring are pivoted.
  • the geometric shape of the elastic arm 102 can for example be obtained by topological optimization using parametric polynomial curves such as Bézier curves.
  • a detailed description of this optimization method is described in the publication WO 2020/016818 of the applicant to obtain an elastic arm 102 whose geometric shape is a Bézier curve or a succession of Bézier curves whose control points have been optimized to take into account, in particular, the dimensions of the spring 100 to be designed as well as obtaining a constant moment of 5% over a predetermined angular range.
  • the geometric shape of the arm 102 used in the present invention can be obtained according to the method described in said publication WO 2020/016818 to produce blades designed, in particular by their shape, to exert a substantially constant moment (constancy of 5%) in a spring comprising a pivoted end and a recessed end as detailed in said publication, but the blade obtained then being used in a spring 100 whose two ends are pivoted in accordance with the present invention.
  • such elastic blades can work in bending (positive stiffness) and in buckling (negative stiffness).
  • Mounting the spring 100 comprising such a blade with its two ends pivoted in accordance with the present invention makes it possible to advantageously modify the behavior of the blade by increasing the buckling.
  • this can very advantageously make it possible to obtain a negative stiffness in at least part of the predetermined range on a blade of constant thickness which had, at the base, a substantially zero stiffness with only one pivoted end, as in the publication WO 2020/016818 .
  • any other form of curve making it possible to obtain an elastic blade which can work in bending (positive stiffness) and in buckling (negative stiffness) so as to present globally a negative or zero stiffness, in particular for a blade of constant section, and more particularly a negative stiffness for a blade of constant section, in at least part of the predetermined range, when the two ends of the spring 100 are pivoted, can be used as an elastic arm in the invention.
  • the spring 100 can be configured to present a negative or zero stiffness in at least part of the predetermined range of winding angles, depending on the intended application for the pivoting member.
  • the predetermined range of winding angles is the predetermined range of the angular positions of the first rotary element 104 with respect to its position of rest, this range being preferably at least 10°, preferably at least 15°, the chosen minimum winding angular position preferably being greater than 5°.
  • spring 100 can be configured to have negative or zero stiffness over substantially all of the predetermined range.
  • the spring 100 can be configured to present a negative stiffness in substantially all of the predetermined range.
  • the spring 100 can be configured to have zero stiffness in substantially all of the predetermined range.
  • the center distance E between the first rotary element 104 and the second rotary element 106 can be advantageously chosen so that the spring 100 has a negative stiffness in said at least part of the predetermined range, preferably in substantially all of the predetermined range.
  • the center distance E varies between 96% and 200% of the developed length of the elastic arm 102.
  • the or each elastic arm 102 has a constant section, and the spring 100 with its two pivoted ends, is configured to have a negative stiffness in said at least part of the predetermined range, preferably in substantially all the predetermined range, unlike a spring of the same shape with one end pivoted and the other end recessed, which has zero stiffness.
  • the center distance E varies between 96% and 200% of the developed length of the elastic arm 102 and the elastic arm 102 is of constant section, the spring 100 with its two pivoted ends having a negative stiffness in said at least part of the predetermined range, preferably in substantially all of the predetermined range.
  • curve C2 of the picture 3 represents the results of a simulation of the evolution of the normalized moment of the spring 100 thus produced as a function of the angular position ⁇ of its first rotary element 104 with respect to its rest position, the two ends of the spring 100 being pivoted in accordance with the invention.
  • curve C1 of the picture 3 represents the evolution of the normalized moment of a similar spring but of which only one end is pivoted, the other end being embedded, as described in the publication WO 2020/016818 .
  • the simulation carried out considers a spring 100 made of an amorphous alloy based on zirconium, titanium, nickel, copper and beryllium, more precisely in a metallic glass of the Vitreloy 1b type, but any suitable material can be used.
  • materials such as other metallic glasses, other alloys such as Nivaflex ® 45/18 (alloy based on cobalt, nickel and chromium), nickel-phosphorus or CK101 (unalloyed structural steel), silicon, typically coated with silicon oxide, or plastic are also suitable. It is important to take into account the ratio between the elastic limit and the Young's modulus of the material to choose the material constituting the elastic arm 102.
  • the stiffness of a spring is the derivative of the function M( ⁇ ) defined respectively by the curves represented on the picture 3 .
  • the Ct2 curve of the figure 4 represents the results of a simulation of the evolution of the normalized stress on the spring 100 as a function of the angular position ⁇ of its first rotary element 104 with respect to its rest position, the two ends of the spring 100 being pivoted in accordance with the invention.
  • the Ct1 curve of the figure 4 represents the evolution of the normalized stress on a similar spring but of which only one end is pivoted, the other end being embedded, as described in the publication WO 2020/016818 .
  • the curves of figure 3 and 4 show that with the spring 100 at both ends pivoted in accordance with the invention, with a center distance E varying from 96% to 200% of the developed length of said elastic arm 102, a negative stiffness is obtained over the range [ ⁇ 2 a , ⁇ 2 b ] with a spring, with an elastic arm 102 of constant section, which, at the base, had zero stiffness and only one pivoted end, the other being embedded.
  • a spring 100 comprising an elastic arm 102 of constant section and mounted in accordance with the invention, it is no longer necessary, to obtain a negative stiffness, to have an elastic arm of variable section as described in the publication WO 2020/016818 .
  • the spring 100 mounted with its two ends pivoted in accordance with the invention makes it possible to simplify the assembly, the watchmaker having only to insert the second rotary element 106 along a pin fixed to the frame, instead of having to lodge the end of the spring between two pins to achieve a recess, as described in the publication WO 2020/016818 .
  • the spring 100 mounted according to the invention requires a minimum winding of approximately 5° to have a negative stiffness, with a wide range of angles over which the stiffness is negative, whereas a spring with a recessed end requires a minimum reinforcement of 18° to present zero stiffness, and over a narrower range.
  • such a spring 100 mounted in accordance with the invention makes it possible to divide the torque almost by a ratio of 3 and to divide the stress almost by 2 with respect to the same spring, one end of which is embedded, at least on a part of the predetermined range.
  • the assembly of the spring 100 according to the invention therefore makes it possible to reduce the torque and the stress significantly compared to a spring at one end embedded, which makes it possible to be able to increase the thickness of the elastic arm 102, without exceeding the allowable stress. of the material.
  • the thickness can be multiplied by approximately 1.4.
  • An increase in the thickness of the elastic arm 102 reinforces the robustness of the mechanism.
  • the torque will be less sensitive to dimensional variations related to the manufacture of the elastic arm.
  • the reduction in stress is appreciable for a material such as silicon.
  • the or each elastic arm 102 has a variable section whose variation is chosen to make it less negative, or even zero depending on the variation of the thickness, the stiffness of the spring 100 in said at least part of the predetermined range, preferably in substantially all of the predetermined range, with respect to an elastic arm of the same shape but of constant section and configured to present a stiffness negative.
  • the figure 5 shows different curves representative of the normalized moment M( ⁇ ) exerted in a spring with pivoted ends and embedded by an elastic arm of constant section of 30 ⁇ m (curve C1) and in the spring 100 at the two pivoted ends in accordance with the invention, by an elastic arm 102 with a constant section of 30 ⁇ m (curve C2) and by arms of different variable sections (other curves) for a center distance of 3 mm corresponding to 125% of the developed length of the elastic arm 102, the spring being moreover identical to the spring 100 described above.
  • the curves located below the curve C2 correspond to an elastic arm 102 whose thickness increases linearly from the first rotary element 104 to the middle of the elastic arm 102 and decreases linearly from the middle of the elastic arm 9 to the second rotary element 106, the thickness in the middle of the elastic arm 102 being 30 ⁇ m for each curve, the thickness at the point of junction with the first or second rotary elements 104, 106 being 29 ⁇ m for the curve C3 under the curve C2, 28 ⁇ m for the curve C4 under curve C2, by 27 ⁇ m for curve C5 under curve C2, and so on by decrementation of 1 ⁇ m.
  • the stiffness becomes less negative (the moment decreases less), or even zero (the moment is substantially constant), in the range of winding angles of interest where the stiffness is negative for an arm of constant section, when the section variation of the elastic arm 102 is increased.
  • the publication WO 2020/016818 showed that an increase in the section variation of the elastic arm of a spring with a pivoted end and a recessed end led to a decrease in the negative stiffness of the spring.
  • the stiffness of the spring 100 mounted in accordance with the invention increases but remains negative when the variation in section of the elastic arm 102 increases but is less than 60%, preferably less than 50%.
  • the stiffness of the spring 100 mounted in accordance with the invention is zero.
  • the elastic arm 102 has a variable section
  • this typically varies in a strictly monotonous manner (it increases or decreases without interruption but not necessarily linearly) over at least a continuous portion of the elastic arm representing 10% , preferably 20%, preferably 30%, preferably 40%, of the (developed) length of the elastic arm.
  • the variation of the section is also chosen to make the stiffness of the elastic arm 102 less negative, or even zero, over the range [ ⁇ 2 a , ⁇ 2 b ] or at least over the part of the predetermined range which intersects with the range [ ⁇ 2 a , ⁇ 2 b ], compared to an elastic arm of the same shape but of constant section.
  • section of the elastic arm which is constant or variable according to the negative or zero stiffness sought in the range of interest.
  • an increase in the variation of the section of the elastic arm makes it possible to reduce the moment as well as the stress, so that the section of the arm can also be adapted according to the intended application for the pivoting member.
  • a spring 100 having an elastic arm 102 of constant section or varying by less than 60% with a center distance E varying from 96% to 200% of the developed length of said elastic arm 102 and its two pivoted ends, a negative stiffness is obtained. on the range [ ⁇ 2 a , ⁇ 2 b ] with a spring which, at the base, had zero stiffness and only one end rotated, the other being embedded.
  • the center distance between the first rotary element 104 and the second rotary element 106 can be chosen so that the spring 100' has zero stiffness in said at least part of the predetermined range, preferably in substantially the entire predetermined range.
  • the center distance E is greater than 200% and less than 300% of the developed length of the elastic arm 102.
  • the or each elastic arm 102 has a constant section, and the spring 100' with its two pivoted ends, is configured to have zero stiffness in said at least part of the predetermined range, preferably in substantially the entire predetermined range.
  • the center distance E is greater than 200% and less than 300% of the developed length of the elastic arm 102 and the elastic arm 102 is of constant section, the spring 100' with its two ends pivoted having zero stiffness in said at least part of the predetermined range, preferably in substantially all of the predetermined range.
  • the applicant has designed another spring 100' as shown in the figure 1 , having a distance between the two ends of the elastic arm 102 of 4 mm, ie a center distance E of 5 mm, equal to 208% of the developed length of the elastic arm 102; the other dimensions of the spring 100' are identical to those of the spring 100 described above.
  • curve C2' of the figure 6 represents the results of a simulation of the evolution of the normalized moment of the spring 100' thus produced as a function of the angular position ⁇ of its first rotary element 104 with respect to its rest position, the two ends of the spring 100' being pivoted in accordance with the invention.
  • curve C1 of the picture 3 which represents the evolution of the normalized moment of a similar spring but of which only one end is pivoted, the other end being embedded, with a center distance E of 5 mm, the moment not varying according to the center distance when the second end is embedded.
  • the Ct2' curve of the figure 7 represents the results of a simulation of the evolution of the normalized stress on the spring 100' as a function of the angular position ⁇ of its first rotary element 104 with respect to its rest position, the two ends of the spring 100' being pivoted in accordance with the invention.
  • the Ct1 curve of the figure 4 which represents the evolution of the normalized stress on a similar spring but of which only one end is pivoted, the other end being embedded, with a center distance E of 5 mm, the stress not varying according to the center distance when the second end is recessed.
  • the curves of figure 6 and 7 show that with the spring 100' at both ends pivoted in accordance with the invention, having an elastic arm 102 of constant cross-section with a center distance E greater than 200% and less than 300% of the developed length of said elastic arm 102, one obtains zero stiffness over the range [ ⁇ 2'a , ⁇ 2'b ] with a spring that basically had zero stiffness and only one end rotated, the other being recessed, but with much reduced moment and stress.
  • a spring 100 'mounted in accordance with the invention makes it possible to divide the torque almost by a ratio of 10 and to divide the stress almost by 4 with respect to the same spring, one end of which is embedded, at least on a part of the predetermined range. As seen above for the spring 100, this makes it possible to increase the thickness of the elastic arm 102, without exceeding the allowable stress of the material.
  • the spring 100' mounted according to the invention requires a minimum winding of approximately 5° to have zero stiffness, whereas the same spring with a recessed end needs to be wound at a minimum of an angle of 18° to have zero stiffness.
  • the spring 100 makes it possible to simplify assembly.
  • the elastic arm 102 is of variable section, the stiffness of the spring 100' with its two ends rotated remaining zero at least in part of the predetermined range, preferably in substantially all of the predetermined range.
  • the variation in the section of the arm does not modify the stiffness of the spring 100' which remains zero at least in part of the predetermined range, preferably within substantially the entire predetermined range.
  • an increase in the variation of the section of the elastic arm makes it possible to reduce the moment as well as the stress, so that the section of the arm can be adapted according to the intended application for the pivoting member and the values desired for timing and stress.
  • the spring 100, 100' mounted according to the invention can be configured so as to adapt its stiffness to the function of the pivoting member with which it is associated.
  • the pivoting member can be subjected to the action of a single spring 100, 100'.
  • the pivoting member can be subjected to the action of at least two springs 100, 100' respectively having zero or negative stiffness at least over the same predetermined range and arranged to generate a torque of pivoting on the pivoting member.
  • said pivoting member is and/or cooperates with, for example, a rocker, a hammer, a lever, a rake, a finger, a slider, a hook, a wheel such as an escape wheel, a regulating member or an energy source.
  • the second rotary element 106 of the spring 100, 100' is pivotally mounted on a frame of the timepiece mechanism.
  • a spring thus mounted in accordance with the invention configured to present a negative stiffness in at least part of the predetermined range, and preferably in substantially all of the predetermined range, as described above, can be associated with a pivoting member which is and/or cooperates with a rocker, a rake or any other cam follower, resting on a cam of variable radius.
  • a pivoting member which is and/or cooperates with a rocker, a rake or any other cam follower, resting on a cam of variable radius.
  • the term "cam follower” means a member which cooperates with the periphery of a cam, typically to read information, without having any function of maintaining the cam in determined positions in normal operation. of the mechanism, unlike for example a jumper or a pawl cooperating with a toothed wheel to position it.
  • the spring mounted and configured in accordance with the invention to have a negative stiffness advantageously makes it possible to exert a constant torque on the cam of variable radius, the negative stiffness compensating for the variation in radius. This makes it possible to have a lower energy consumption and to limit the jolts.
  • a spring thus mounted in accordance with the invention configured to have zero stiffness in at least part of the predetermined range, and preferably in substantially all of the predetermined range, as described above, can be associated with a pivoting member which is, for example, a rocker without support, a player, a hook, or a wheel such as an escapement wheel.
  • a pivoting member which is, for example, a rocker without support, a player, a hook, or a wheel such as an escapement wheel.
  • the pivoting member when the pivoting member cooperates with an escape wheel, it can be arranged to be subjected to the action of two springs mounted in accordance with the invention, configured to respectively have zero stiffness at least over the same predetermined range as described above, of slightly different thicknesses and having elastic arms of opposite directions, the subtraction of the two torques at zero stiffness generating on the pivoting member a very low constant pivoting torque.
  • Zero stiffness is obtained according to the different configurations described above.
  • Such a pivoting member is grafted onto the escape wheel to deliver a constant torque at each alternation.
  • the spring of zero stiffness can be mounted directly on said player, so that the axis of the rocker of the player has a constant torque return spring.
  • the gear opposite the slider will always see the same effort. This makes it possible to make the machining imperfections of the player and of said gear less noticeable.
  • a spring with zero stiffness can be mounted directly on a shaft without support, as a source of energy or as a return torque for a function.
  • the spring of zero stiffness can be mounted directly on the axis of said hook.
  • Such a spring of zero stiffness in accordance with the invention has a very low torque which is perfectly suited to the pivoting torque corresponding to this application.
  • the figure 8 represents an embodiment of a watch mechanism comprising a pivoting member according to the invention in which the second rotary element 106 of the spring 100 is pivotally mounted on a frame 1a of said watch mechanism.
  • the pivoting member cooperates with a rocker resting on a cam of variable radius and the spring 100, with an elastic arm 102 of constant section, is configured to present a negative stiffness over the entire predetermined range
  • the mechanism 1 is an instantaneous minute counter mechanism of a chronograph.
  • Said mechanism 1 is mounted on the frame 1a, and comprises a rocker 2 pivoted in O and having a feeler 3 cooperating with a snail cam 4 mounted on, and driven by, the chronograph axis 5.
  • This chronograph axis 5 carries its upper end the chronograph seconds indicator hand 6 and is integral in rotation with the chronograph wheel 7 and the heart for resetting the chronograph seconds 8.
  • the rocker 2 is held in abutment against the periphery of the snail cam 4 by a rocker return spring 100 acting on the axis 10 of a finger 11, this finger 11 itself acting on the rocker 2.
  • the cooperation between the finger 11 and the rocker 2 is of the bearing type.
  • the finger 11 indeed interacts with the wall of a recess 12 of the rocker 2 in the manner of meshing, almost without friction. Rocker 2 and finger 11 thus rotate in opposite directions.
  • the finger 11 constitutes the pivoting member mounted on its pivot axis 10 and subjected to the action of its spring 100.
  • the first rotary element 104 of the spring 100 is driven onto the axis 10 of the finger 11 and the second rotary element 106 is pivotally mounted on a pin 108 secured to frame 1a.
  • a hook 13 is pivoted at P on the free end of the rocker 2 and is subjected to the action of a hook return spring 14, mounted on the rocker 2, tending to apply the beak 15 of the hook 13 against the wolf tooth toothing of a 16 minute counter wheel.
  • the hook return spring 14 could be replaced by a spring configured in accordance with the invention to have zero stiffness over a predetermined range and whose first rotary element is mounted directly on the axis of the hook, the second rotary element being mounted on a pin secured to the frame 1a.
  • a chronograph minute indicator 18 such as a hand (as shown) or disc, displaying the chronograph minutes in cooperation with the chronograph dial.
  • a chronograph minute reset core 19 is integral in rotation with the minute counter wheel 16.
  • the minute counter wheel 16 is held in determined angular positions between its successive actuations by a jumper 20 on which acts a jumper return spring 21.
  • the snail cam 4 has a slot 22 in its end part, in accordance with the teaching of the patent application EP 2241944 , but it could have a more classic shape, without this slot 22.
  • the snail cam 4 has a variable radius between its lower part B and its upper part H, so that at each turn of rotation of the snail cam 4, the feeler 3 of the rocker 2 slides from the lower part B towards the part high H of cam 4.
  • Rocker 2 rises gradually by rotating finger 11 in the opposite direction, spring 100 winding up as it goes.
  • the spring 100 is arranged to work in a predetermined range of winding angles, said spring being shaped according to the invention to present here a negative stiffness throughout the predetermined range in order to compensate for the lever arm effect of the cam snail. More specifically in relation to the spring 100 corresponding to the picture 3 , said spring 100 is of constant section, configured so that, at each revolution of the snail cam 4 against the return action of the elastic arm 102, the first rotary element 104 moves in a predetermined range of angular positions with respect to in its rest position, this range being included in the range of angular positions [ ⁇ 2 a , ⁇ 2 b ] associated with the spring 100 in which the stiffness of the elastic arm 102 is negative.
  • said predetermined range is constituted by this range of angular positions [ ⁇ 2 a , ⁇ 2 b ] where the stiffness is negative at each point.
  • the length of the predetermined range is defined by the difference in radius between the upper part H and the lower part B of the cam 4, the position of the rocker 2 and that of the finger 11. In the example illustrated, it is 3 °, which leaves a wide choice of the winding angle at the time of assembly.
  • the first rotary element 104 is positioned angularly when it is mounted on the axis 10 of the finger 11 so that the spring 100 is armed with ⁇ arm degrees when the feeler 3 of the rocker 2 is on the lower part B of the snail cam 4, this value ⁇ arm being chosen within the predetermined range, and may for example be the lower limit of the aforementioned predetermined range, ie here 5°. It is also possible to choose a value ⁇ arm of 9° for example in order to be situated in a part of the predetermined range, for which the stiffness is even more negative.
  • Such a spring 100 makes it possible to fully compensate for the increase in the lever arm of the force applied to the cam 4 by the rocker 2 on one revolution of rotation of this cam during the movement of the rocker 2 from the lower part B to the upper part H, with an elastic arm 102 of constant section, without having to use an arm of variable section as in the publication WO 2020/016818 .
  • This makes it possible to make constant the torque which it exerts indirectly on the cam 4 and thus, on the one hand, to improve the regularity of the oscillations of the regulator organ of the chronograph and therefore the precision of the measurement and, on the other hand, decrease energy consumption.
  • the thickness of the elastic arm 102 could be increased from a 28 ⁇ m metallic glass blade to a 40 ⁇ m blade to obtain the same torque without exceeding the allowable stress of the material.
  • Mounting the spring 100 in accordance with the invention is simplified, requiring only a single pin 108 and the windage is 9° against 18° for the spring at one end pivoted and the other end embedded.
  • the use of the intermediate finger 11 between the spring 100 and the rocker 2 makes it possible, by acting on the lever arms, to reduce the size of the mechanism 1 for a given restoring torque applied to the rocker 2.
  • this finger 11 could be removed and spring 100 could act more directly on rocker 2, the pivoting member then being the rocker itself.
  • the first rotating element 104 could be mounted directly on the axis of rocker 2.
  • Spring 100 could also form a single piece with rocker 2.
  • the second rotary element 106 of the spring 100, 100' is pivotally mounted on a movable element of the pivoting member, said movable element being arranged to be movable relatively with respect to the axis pivoting of said pivoting member.
  • pivoting member 110 which in this example is more specifically subjected to the action of a plurality of springs 100, 100' respectively having zero or negative stiffness at least over the same predetermined range and arranged to generate a pivoting torque on said pivoting member 110.
  • the pivoting member 110 comprises a hub 112 secured to the pivot axis (not shown) of said pivoting member 110, and an annular rim 114 constituting the movable element of the pivoting member 114.
  • Each of the second rotating elements 106 of the springs 100, 100' is pivotally mounted on the rim 114, for example by means of pins or tenons 116 distributed around the periphery of the rim 114.
  • the tenons 116 have the advantage of avoiding the out-of-plane displacement of the arms 102 of the springs 100, 100'.
  • the pins or tenons 116 can be attached or form a single piece with the serge 114.
  • the first rotary elements 104 of the springs 100, 100' are all fixed at least in rotation to the pivot axis of the pivoting member 110.
  • the first rotary elements 104 of the springs 100, 100' are advantageously arranged to form a single piece which constitutes the hub 112 of the pivoting member 110.
  • the hub 112 formed by the union of the first rotary elements 104, and all of the arms 102 terminated by the second rotary elements 106 form a single one-piece piece.
  • each arm 102 can be made independently of the hub, and then assembled to the hub 112.
  • the hub 112 can be mounted integrally on the pivot axis, for example by driving or other equivalent means, or be made in one piece with the pivot axis of the pivoting member 110.
  • the pivoting member 110 is obtained by assembling on the rim 114 each of the second rotary elements 106 of the arms 102 carried by the hub 112 by means of its tenon 116.
  • the negative or zero stiffness of the springs 100, 100' as well as for example the thickness of the blades of the arms 102 of the pivoting member 110 are chosen according to the desired application of said pivoting member 110.
  • the springs 100, 100' can have zero or negative stiffness, and preferably zero stiffness, obtained according to the various possibilities described above, with thicker blades than for a similar pivoting member but with second embedded rotating elements, so as to obtain a large constant torque, allowing an application as a source of energy. Thinner blades make it possible to obtain a very low torque for applications of the regulating organ or very low energy source type.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Springs (AREA)

Claims (19)

  1. Uhrwerkmechanismus (1), der ein schwenkbares Organ umfasst, das auf einer Schwenkachse gelagert ist und der Wirkung mindestens einer Feder (100, 100') unterliegt, die dazu gestaltet ist, in einem vorbestimmten Bereich von Spannungswinkeln zu arbeiten, wobei die Feder (100, 100') mindestens einen elastischen Arm (102) umfasst, der an einem seiner Enden ein erstes drehbares Element (104) aufweist, das mit der Schwenkachse des schwenkbaren Organs mindestens drehfest ist, wobei die Feder (100, 100') in mindestens einem Teil des vorbestimmten Bereichs eine Steifigkeit aufweist, die gleich Null oder negativ ist, dadurch gekennzeichnet, dass der elastische Arm (102) an dem anderen seiner Enden ein zweites drehbares Element (106) aufweist, das schwenkbar gelagert ist.
  2. Uhrwerkmechanismus (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Steifigkeit der Feder (100, 100') in im Wesentlichen dem gesamten vorbestimmten Bereich gleich Null oder negativ ist.
  3. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der oder jeder elastische Arm (102) eine gewundene Form aufweist.
  4. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die geometrische Form des oder jedes elastischen Arms (102) eine Bezierkurve oder eine Folge von Bezierkurven ist.
  5. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Achsabstand (E) zwischen dem ersten drehbaren Element (104) und dem zweiten drehbaren Element (106) derart gewählt ist, dass die Feder (100) in dem mindestens einen Teil des vorbestimmten Bereichs, vorzugsweise in im Wesentlichen dem gesamten vorbestimmten Bereich, eine negative Steifigkeit aufweist.
  6. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Achsabstand zwischen 96 % und 200 % der expandierten Länge des elastischen Arms (102) variiert.
  7. Uhrwerkmechanismus (1) nach einem der Ansprüche 5 und 6, dadurch gekennzeichnet, dass der oder jeder elastische Arm (102) einen konstanten Querschnitt aufweist, wobei die Steifigkeit der Feder (100) in dem mindestens einen Teil des vorbestimmten Bereichs, vorzugsweis in im Wesentlichen dem gesamten vorbestimmten Bereich, negativ ist.
  8. Uhrwerkmechanismus (1) nach einem der Ansprüche 5 und 6, dadurch gekennzeichnet, dass der oder jeder elastische Arm (102) einen veränderlichen Querschnitt aufweist, dessen Veränderung derart ausgewählt ist, dass die Steifigkeit der Feder (100) in dem mindestens einen Teil des vorbestimmten Bereichs, vorzugsweise in im Wesentlichen dem gesamten vorbestimmten Bereich, in Bezug auf einen elastischen Arm mit der gleichen Form, aber mit konstantem Querschnitt, weniger negativ oder sogar gleich Null gemacht wird.
  9. Uhrwerkmechanismus (1) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Achsabstand (E) zwischen dem ersten drehbaren Element (104) und dem zweiten drehbaren Element (106) derart ausgewählt ist, dass die Feder (100, 100') in dem mindestens einen Teil des vorbestimmten Bereichs, vorzugsweise in im Wesentlichen dem gesamten vorbestimmten Bereich, eine Steifigkeit von gleich Null aufweist.
  10. Uhrwerkmechanismus (1) nach Anspruch 9, dadurch gekennzeichnet, dass der Achsabstand (E) größer als 200 % und kleiner als 300 % der expandierten Länge des elastischen Arms (102) ist.
  11. Uhrwerkmechanismus (1) nach einem der Ansprüche 9 und 10, dadurch gekennzeichnet, dass der oder jeder elastische Arm (102) einen konstanten Querschnitt aufweist, wobei die Steifigkeit der Feder (100') in dem mindestens einen Teil des vorbestimmten Bereichs, vorzugsweise in im Wesentlichen dem gesamten vorbestimmten Bereich, gleich Null ist.
  12. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das schwenkbare Organ der Wirkung von mindestens zwei Federn (100, 100') unterliegt, die mindestens in einem gleichen vorbestimmten Bereich jeweils eine Steifigkeit aufweisen, die gleich Null oder negativ ist, und dazu gestaltet sind, ein Schwenkmoment auf das schwenkbare Organ zu erzeugen.
  13. Uhrwerkmechanismus (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das schwenkbare Organ eine Wippe (2), ein Hammer, ein Hebel, ein Rechen, ein Finger (11), ein Kupplungstrieb, ein Haken, ein Rad, ein Regulierorgan, eine Energiequelle ist und/oder damit zusammenwirkt.
  14. Uhrwerkmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das zweite drehbare Element (106) der Feder (100, 100') schwenkbar auf einem Gestell (1a) des Uhrwerkmechanismus (1) gelagert ist.
  15. Uhrwerkmechanismus (1) nach einem der Ansprüche 13 bis 14, dadurch gekennzeichnet, dass das schwenkbare Organ eine Wippe (2), die auf einer Kurvenscheibe (4) mit veränderlichem Radius aufliegt, ist und/oder damit zusammenwirkt, wobei die Feder (100) eine negative Steifigkeit aufweist.
  16. Uhrwerkmechanismus (1) nach einem der Ansprüche 13 bis 14, dadurch gekennzeichnet, dass das schwenkbare Organ eine Wippe ohne Auflage, ein Kupplungstrieb, ein Haken, ein Rad ist, wobei die Feder (100, 100') eine Steifigkeit von gleich Null aufweist.
  17. Uhrwerkmechanismus (1) nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass das zweite drehbare Element (106) der Feder (100, 100') schwenkbar auf einem beweglichen Element des schwenkbaren Organs (110) gelagert ist, das dazu gestaltet ist, relativ in Bezug auf die Schwenkachse des schwenkbaren Organs (110) beweglich zu sein.
  18. Uhrwerkmechanismus (1) nach Anspruch 17, dadurch gekennzeichnet, dass das schwenkbare Organ (110) der Wirkung mehrerer Federn (100, 100') unterliegt, die jeweils eine Steifigkeit aufweisen, die über mindestens einen gleichen vorbestimmten Bereich gleich Null oder negativ ist, und dazu gestaltet sind, auf dem schwenkbaren Organ (110) ein Schwenkmoment zu erzeugen, dadurch, dass das schwenkbare Organ (110) eine Nabe (112), die fest mit der Schwenkachse verbunden ist, und einen Fußkreis (114) umfasst, der das bewegliche Element des schwenkbaren Organs (110) bildet, und dadurch, dass jedes von den zweiten drehbaren Elementen (106) der Federn (100, 100') schwenkbar auf dem Fußkreis (114) gelagert ist, wobei die ersten drehbaren Elemente (104) der Federn (100, 100') dazu gestaltet sind, ein einziges Teil zu bilden, das die Nabe (112) des schwenkbaren Organs (110) bildet.
  19. Uhr, die einen Uhrwerkmechanismus (1) nach einem der Ansprüche 1 bis 18 umfasst.
EP20173411.8A 2020-05-07 2020-05-07 Uhrwerkmechanismus, das ein schwenkorgan umfasst Active EP3907563B1 (de)

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EP20173411.8A EP3907563B1 (de) 2020-05-07 2020-05-07 Uhrwerkmechanismus, das ein schwenkorgan umfasst

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EP3907563B1 true EP3907563B1 (de) 2022-09-14

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3619579B1 (de) * 2017-05-03 2021-06-09 Patek Philippe SA Genève Uhrvorrichtung mit positionierorgan

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH700753B1 (fr) 2009-04-15 2014-03-14 Patek Philippe Sa Geneve Mécanisme de compteur instantané et came escargot pour un tel mécanisme.
EP2706416B1 (de) * 2012-09-07 2015-11-18 The Swatch Group Research and Development Ltd Flexibler Anker mit konstanter Kraft
EP3483666A1 (de) * 2017-11-10 2019-05-15 Patek Philippe SA Genève Vorrichtung zur rotationssteuerung einer beweglichen komponente
EP3598242A1 (de) 2018-07-19 2020-01-22 Patek Philippe SA Genève Uhrwerksmechanismus mit nocke

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3619579B1 (de) * 2017-05-03 2021-06-09 Patek Philippe SA Genève Uhrvorrichtung mit positionierorgan

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