EP3824354A1 - Mecanisme horloger a came - Google Patents
Mecanisme horloger a cameInfo
- Publication number
- EP3824354A1 EP3824354A1 EP19766359.4A EP19766359A EP3824354A1 EP 3824354 A1 EP3824354 A1 EP 3824354A1 EP 19766359 A EP19766359 A EP 19766359A EP 3824354 A1 EP3824354 A1 EP 3824354A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- clock mechanism
- cam
- return spring
- elastic arm
- cam follower
- 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.)
- Pending
Links
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
-
- 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
-
- 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
- G04F7/0866—Special arrangements
Definitions
- the present invention relates to a cam clock mechanism.
- Mechanisms are known in watchmaking for the instantaneous driving of an indicator comprising a spiral cam known as a snail cam or snail cam against which a rocker rests 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.
- This variation in torque increases the energy consumption and affects the regularity of the oscillations of the regulating body of the watch and therefore the accuracy of the measurement.
- the present invention aims to alleviate these problems and proposes for this purpose a timepiece mechanism according to claim 1, namely a timepiece mechanism comprising a cam intended to be driven in rotation, a cam follower and a return spring arranged to hold the follower cam resting against the cam, the return spring being arranged to work within a predetermined range of winding angles during each rotation of the cam, characterized in that the stiffness of the return spring is zero or negative in at least part of the predetermined range.
- the invention further provides a timepiece, such as a wristwatch or a pocket watch, comprising this timepiece mechanism.
- FIG. 1 is a plan view from below of a cam clock mechanism according to an exemplary embodiment of the invention
- FIG. 2 is a plan view from above of a part of the timepiece mechanism according to the invention comprising a return spring;
- - Figure 3 is a plan view from above of a variant of said part;
- - Figure 4 is a schematic graphic representation of the elastic return moment exerted in the part illustrated in Figure 2;
- - Figure 5 shows the coordinates of points defining a particular shape of an elastic arm constituting the return spring
- - Figure 6 is a graphic representation of the elastic return moment exerted in the part illustrated in Figure 2 by the return spring having the shape as shown in Figure 5;
- FIG. 7 is a graphic representation of a standardized elastic return moment exerted in the part illustrated in Figure 2 by an elastic arm having the shape as shown in Figure 5 according to different variants of the elastic arm, namely such constant section arm (curve C1) and such a variable section arm (other curves), the section varying according to a first mode of variation;
- FIG. 8 is a graphic representation of a standardized elastic return moment exerted in the part illustrated in Figure 2 by an elastic arm having the shape as shown in Figure 5 according to different variants of the elastic arm, namely such constant section arm (curve C1) and such a variable section arm (other curves), the section varying according to a second mode of variation.
- stiffness is understood to mean tangential stiffness.
- FIG. 1 a clockwork mechanism 1 according to an exemplary embodiment of the invention, mounted on a frame 1 a.
- the mechanism 1 is an instantaneous minute counter mechanism of a chronograph. It includes 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 at its upper end the hand indicating the seconds of chronograph 6 and is integral in rotation with the chronograph wheel 7 and the chronograph seconds reset heart 8.
- the lever 2 is held in abutment against the periphery of the snail cam 4 by a lever return spring 9 acting on the axis 10 of a finger 11, this finger 11 itself acting on the lever 2.
- the cooperation between the finger 11 and the lever 2 is of the rolling type. Finger 11 indeed interacts with the wall of a recess 12 of the rocker 2 in the manner of a meshing, almost without friction. The rocker 2 and the finger 11 thus rotate in opposite directions.
- a hook 13 is pivoted at P on the free end of the lever 2 and is subjected to the action of a hook return spring 14, mounted on the lever 2, tending to apply the spout 15 of the hook 13 against the wolf teeth teeth of a minute counter wheel 16.
- the axis 17 of the minute counter wheel 16 carries a chronograph minute indicator 18, such as a hand (as shown) or a disc, displaying the chronograph minutes in cooperation with the chronograph dial.
- a chronograph minute resetting heart 19 is integral in rotation with the minute counter wheel 16.
- the minute counter wheel 16 is held in angular positions determined 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 terminal part, in accordance with the teaching of patent application EP 2241944, but it could have a more conventional shape, without this slot 22.
- the rocker 2 and its return spring 9 are armed as the probe 3 slides from the bottom part B towards the top part H of the cam 4.
- Each minute, the probe 3 and with it all the rocker 2 falls from the upper part H to the lower part B of the snail cam 4 under the action of the rocker return spring 9.
- the hook 13 advances the wheel one step of the minute counter 16 to instantly change the value indicated by the chronograph minute indicator 18.
- the hook 13 passes from the the minute counter wheel 16 in which it was located during the fall in the previous crank against the action of its return spring 14, to again advance the minute counter wheel 16 during one step the next fall of rocker 2.
- the rocker return spring 9 is specially shaped to improve the constancy of the torque or moment of force which it exerts (indirectly) on the cam 4 and thus, on the one hand, improve the regularity of the oscillations of the regulating organ of the chronograph and therefore the accuracy of the measurement and, on the other hand, reduce energy consumption.
- the rocker return spring 9 is in the form of an elastic arm or blade forming part of a part 23 further comprising a base 24 and a rotary element 25, the elastic arm 9 connecting the base 24 to the rotary element 25, only the elastic arm 9 deforms during the operation of the mechanism 1.
- the base 24 is fixed, for example by means of pins 26, to the frame 1 a.
- the rotary element 25, intended to rotate on itself, is eccentric with respect to the base 24.
- the rotary element 25 is mounted on the axis 10 of the finger 1 1 and is integral in rotation with this finger 1 1.
- the rotary member 25 is the finger 1 1 itself, in other words the base 24, the elastic arm 9 and the finger 1 1 form the part 23 .
- the part 23 is typically monobloc. 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
- FIG. 2 represents this isolated part 23.
- the part 23 Due to the shape of its elastic arm 9, the part 23 has a preferred direction of rotation of its rotary element 25 relative to its base 24, this direction being defined as that which allows, from a state of rest, the isolated piece 23 in which its elastic arm 9 is at rest, the greatest angular displacement relative of the rotary element 25 with respect to the base 24.
- This preferred direction of rotation is counterclockwise in FIG. 1 and clockwise in FIG. 2.
- FIG. 4 illustrates the evolution M (q) of the elastic return moment exerted by the elastic arm 9 in the piece 23 isolated as a function of the angular position Q of the rotary element 25 relative to the base 24.
- the elastic return moment increases rapidly with the angular position Q; beyond this first value qi, the part 23 is in a substantially stable phase. Indeed, between this first value qi and a second value 02, the elastic return moment is substantially constant with respect to the angular position Q.
- substantially constant moment is meant a moment not varying by more than 10%, preferably 5%, more preferably 3%, it being understood that this percentage can be further reduced. More precisely, let Mmin and M Imax respectively be the values of the minimum and maximum moments exerted in the isolated piece 23 on a given range [qi, Q2] of angular positions of the rotary element 25 relative to the base 24, the moment exerted in this isolated piece 23 is substantially constant as soon as the inequality "(Mmax-
- the elastic return moment exerted by the elastic arm 9 in the isolated part 23 locally reaches a maximum for an angular position 0 a , then decreases in the range of angular positions between the values 0 a and 0b, where 0 a and 0b are between 01 and 02;
- the isolated piece 23 having a curve M (0) of the type shown in FIG. 4 differs from conventional elastic structures. Its properties are based on a sinuous shape of its elastic arm 9 which deforms so as to generate a substantially constant elastic return moment (the curve M (0) has a plateau between 01 and Q2) over a predetermined range of angular positions of sound. rotary element 25 relative to its base 24. Obtaining such an elastic arm 9 requires a specific and parameterized design. It can for example be obtained by topological optimization by applying the teaching of the publication "Design of adjustable constant-force forceps for robot-assisted surgical manipulation", Chao-Chieh Lan et al., 2011 IEEE International Conference on Robotics and Automation, Shanghai International Conference Center, May 9-13, 2011, China.
- the topological optimization discussed in the above article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic arm.
- the geometric shape of the elastic arm 9 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the part 23 to be designed as well as a constraint "(Mmax- Mmin) / ((Mmax + Mmin) / 2) £ 0.05 ”.
- the inequality "(Mmax-Mmin) / ((Mmax + Mmin) / 2) £ 0.05" corresponds to a constant elastic return moment of 5% over an angular range.
- the elastic arm or rocker return spring 9 is designed, in particular by its shape, to exert, in the part 23, a substantially constant elastic return moment (constancy of 5%) over a range of angular positions of the rotary element 25 relative to the base 24 of at least 10 °, preferably at least 15 °, more preferably at least 20 °.
- the geometric shape of the elastic arm 9 is defined by the set of points
- Qix and Qiy are the x and y coordinates of the Qi control points, respectively.
- Curvilinear length of elastic arm 9 2.4 mm;
- Thickness (width) of the elastic arm 9 25.6 ⁇ m
- control points Qo, Qi, Q2, Q3, Q4, Q5, ⁇ 6 were used.
- the coordinates of these control points are given in table 1 below.
- Table 1 Coordinates of the Qo to OQ control points.
- the Bézier curve has been broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on the control points Qo to Cb and a second segment corresponding to a curve of Bézier of order 4 based on the control points Cb to Cb.
- Table 2 Coordinates of crossing points of the optimized elastic arm.
- the graph in FIG. 5 shows the external surface of the rotary element 25, the internal surface of the base 24 and the elastic arm 9 of the particular part 23 that the applicant has designed, the geometry of the arm 9 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.
- FIG. 6 represents the results of a simulation of the evolution of the elastic return moment of the particular part 23 thus produced as a function of the angular position Q of its rotary element 25 relative to its base 24.
- the simulation carried out considers a part 23 produced in 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 (non-alloy structural steel ), silicon, typically coated with silicon oxide, or plastic are also suitable. It is important to take into account the relationship between the elastic limit and the Young's modulus of the material to choose the material constituting the elastic arm 9.
- the stiffness of the part 23, more precisely of its elastic arm 9, is the derivative of the function M (0) defined above.
- the stiffness is zero at the angular positions 0 a and 0b and negative between these positions 0 a and 0b.
- the part 23 is therefore arranged so that, at each rotation of the snail cam 4 against the return action of the elastic arm or rocker return spring 9, the rotary element 25 moves in a predetermined range of angular positions relative to the base 24, this range being included in the range of positions [qi, Q2] associated with the part 23 and comprising at least part of the range of positions [0 a , 0b] in which the stiffness of the elastic arm 9 is zero or negative.
- said predetermined range is included in the range [0 a , 0b] or constituted by the latter. More preferably, said predetermined range is included in the range] 0 a , 0b [where the stiffness is negative at each point.
- the rotary element 25 is angularly positioned during its mounting on the axis 10 of the finger 11 so that the rocker return spring 9 is armed by 0arm degrees when the feeler 3 of the rocker 2 is located on the lower part B of the snail cam 4, this value 0arm being the lower limit of the aforementioned predetermined range.
- the rotary element 25 may include a mark 27 to be aligned for example with the finger 11.
- the part 23 is shown in its rest position, before its pre-winding.
- 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 lever 2 and that of the finger 11. In the example illustrated, it is 3 °.
- the average intensity of the force applied to the snail cam 4 by the rocker return spring 9 via the finger 11 and rocker 2 on a rotation of the snail cam 4 can be reduced compared to a traditional rocker return spring, for the same force applied to the cam 4 when the probe 3 is on the lower part B, thereby reducing the energy required to rotate the snail cam 4.
- the negative stiffness of the rocker return spring 9 also makes it possible to at least partially compensate for the variation of the lever arm of the force applied to the cam 4 by the rocker 2 on a rotation of this cam, more precisely the increase in the lever arm of the force applied to the cam 4 during the movement of the rocker 2 from the lower part B to the upper part H. A smaller variation in the torque required to rotate the cam 4 and therefore better timing can thus be obtained.
- FIG. 7 shows different curves representative of a normalized moment of force M (q) exerted by the elastic arm 9 in the isolated part 23 for different variations in section of the elastic arm 9.
- the highest curve, designated by C1 corresponds to an elastic arm 9 of constant section and thickness (width) 30 ⁇ m.
- the curves located below the curve C1 correspond to an elastic arm 9 whose thickness increases linearly from the rotary element 25 to the base 24, the thickness at the point of junction with the base 24 being 30 ⁇ m for each curve, the thickness at the junction point with the rotary element 25 being 29 ⁇ m for the first curve C2 under the curve C1, 28 ⁇ m for the second curve C3 under the curve C1, 27 ⁇ m for the third curve C4 under curve C1, and so on by decrementing by 1 ⁇ m. It is noted that, for at least the first curves, the stiffness decreases (the force moment decreases more) in the range of winding angles of interest where the stiffness is negative when the variation in section is increased.
- FIG. 8 shows different curves representative of a normalized force moment M (q) exerted by the elastic arm 9 in the isolated part 23.
- the highest curve, designated by C1 corresponds to an elastic arm 9 of constant section and 30 ⁇ m thick.
- the curves located below the curve C1 correspond to an elastic arm 9 whose thickness increases linearly from the rotary element 25 in the middle of the elastic arm 9 and decreases linearly from the middle of the elastic arm 9 to the base 24, l ' thickness in the middle of the elastic arm 9 being 30 ⁇ m for each curve, the thickness at the junction point with the rotary element 25 and at the junction point with the base 24 being 29 ⁇ m for the first curve C2 ′ under the curve C1, 28 ⁇ m for the second curve C3 'under the curve C1, 27 ⁇ m for the third curve C4' under the curve C1, and so on by decrementing by 1 ⁇ m.
- this mode of variation of the section of the elastic arm 9 also makes it possible to adjust the negative stiffness in order for example to completely or almost completely compensate for the effect of the increase in the lever arm of the force applied to the snail cam 4 by rocker 2 during its movement from the lower part B to the upper part H.
- the elastic arm 19 in cases where the elastic arm 19 has 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 make the stiffness of the elastic arm 19 more negative over the range [0 a , 0b] or at least over the part of the predetermined range which overlaps with the range [0 a , 0b] , relative to an elastic arm of the same shape as the arm 19 but of constant section.
- the rocker return spring or elastic arm 9 can have a shape different from that illustrated in FIGS. 1 and 2. It can in particular take a shape 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 rocker return spring 9 could comprise several elastic arms connecting the base 24 to the rotary element 25, to the like the devices described in the two articles "Design of adjustable constant-force forceps for robot-assisted surgical manipulation” and “Functional joint mechanisms with constant-torque outputs” mentioned above.
- a single elastic arm 9 is sufficient since it has no guiding function - the rotary element 25 is guided by the axis 10 of the finger 1 1 - but only performs an elastic recall function. It will also be noted that making the rocker return spring 9 in the form of a single elastic arm has the advantage of being more compact.
- the choice of the number of elastic arms (s), their length and their thickness determines the intensity of the force produced. You can also play on the inclination of the elastic arm (s) relative to the rotary element 25 (in the plane of the part 23) to modify the intensity of the force produced.
- the present invention is not limited to a minute counter mechanism or a snail cam. It is also not limited to an instantaneous action mechanism, causing a jump movement of an indicator or other movable member. It can be applied to any watch mechanism comprising a cam which successively, one or more times per revolution, arms and disarms (partially) a rocker, a rake or other cam follower.
- the term "cam follower” means a member which cooperates with the periphery of a cam, typically for reading information, without having any function of maintaining the cam in positions determined by normal operation of the mechanism, unlike for example a jumper or a pawl cooperating with a toothed wheel to position it.
- the use of the intermediate finger 11 between the rocker return spring 9 and the rocker 2 allows, by playing on the lever arms, to reduce the size of the mechanism 1 for a given return torque applied to the rocker 2.
- this finger 11 could be removed and the rocker return spring 9 could act more directly on the rocker 2, for example the rotary element 25 could be mounted on the axis of the rocker 2.
- the return spring of lever 9 could also form a single piece with lever 2, or even be an integral part of the lever and guide in rotation relative to a base a rigid end acting as a cam follower.
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- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Measurement Of Unknown Time Intervals (AREA)
- Springs (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP18184529.8A EP3598242A1 (fr) | 2018-07-19 | 2018-07-19 | Mecanisme horloger a came |
PCT/IB2019/056140 WO2020016818A1 (fr) | 2018-07-19 | 2019-07-18 | Mecanisme horloger a came |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3824354A1 true EP3824354A1 (fr) | 2021-05-26 |
Family
ID=63012933
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18184529.8A Withdrawn EP3598242A1 (fr) | 2018-07-19 | 2018-07-19 | Mecanisme horloger a came |
EP19766359.4A Pending EP3824354A1 (fr) | 2018-07-19 | 2019-07-18 | Mecanisme horloger a came |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18184529.8A Withdrawn EP3598242A1 (fr) | 2018-07-19 | 2018-07-19 | Mecanisme horloger a came |
Country Status (2)
Country | Link |
---|---|
EP (2) | EP3598242A1 (fr) |
WO (1) | WO2020016818A1 (fr) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3907563B1 (fr) | 2020-05-07 | 2022-09-14 | Patek Philippe SA Genève | Mécanisme horloger comprenant un organe pivot |
EP3955064A1 (fr) | 2020-08-12 | 2022-02-16 | Patek Philippe SA Genève | Composant horloger comportant une ouverture destinee au chassage d'un axe |
EP4325301A1 (fr) | 2022-08-17 | 2024-02-21 | Patek Philippe SA Genève | Mécanisme horloger comprenant un organe horloger rotatif et un dispositif à raideur angulaire prédéfinie |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1746470A1 (fr) | 2005-07-20 | 2007-01-24 | Breitling AG | Pièce d'horlogerie à mécanisme de quantième |
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. |
CH700753B1 (fr) | 2009-04-15 | 2014-03-14 | Patek Philippe Sa Geneve | Mécanisme de compteur instantané et came escargot pour un tel mécanisme. |
CH702804B1 (fr) * | 2010-03-10 | 2014-07-31 | Patek Philippe Sa Genève | Mécanisme transformateur de couple. |
EP2645189B1 (fr) * | 2012-03-29 | 2016-02-03 | Nivarox-FAR S.A. | Mécanisme d'échappement flexible |
EP2952973B1 (fr) * | 2013-04-30 | 2017-12-06 | Audemars Piguet (Renaud et Papi) SA | Mécanisme de saut instantané pour pièce d'horlogerie |
-
2018
- 2018-07-19 EP EP18184529.8A patent/EP3598242A1/fr not_active Withdrawn
-
2019
- 2019-07-18 EP EP19766359.4A patent/EP3824354A1/fr active Pending
- 2019-07-18 WO PCT/IB2019/056140 patent/WO2020016818A1/fr active Application Filing
Also Published As
Publication number | Publication date |
---|---|
EP3598242A1 (fr) | 2020-01-22 |
WO2020016818A1 (fr) | 2020-01-23 |
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