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
  • G04B11/00—Click devices; Stop clicks; Clutches
  • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
  • G04B11/028—Devices allowing the motion of a rotatable part in only one direction with friction member, e.g. click spring
• • 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
  • G04B11/006—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices)
  • G04B11/008—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices) with friction members, e.g. click springs or jumper
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B19/00—Indicating the time by visual means
  • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
  • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
  • G04B19/247—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator disc-shaped
  • G04B19/253—Driving or releasing mechanisms
  • G04B19/25333—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement
  • G04B19/25353—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement driven or released stepwise by the clockwork movement
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B19/00—Indicating the time by visual means
  • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
  • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
  • G04B19/247—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator disc-shaped
  • G04B19/253—Driving or releasing mechanisms
  • G04B19/25333—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement
  • G04B19/25373—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement driven or released stepwise by an energy source which is released at determined moments by the clockwork movement
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
  • G05G5/00—Means for preventing, limiting or returning the movements of parts of a control mechanism, e.g. locking controlling member
  • G05G5/06—Means for preventing, limiting or returning the movements of parts of a control mechanism, e.g. locking controlling member for holding members in one or a limited number of definite positions only
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T74/00—Machine element or mechanism
  • Y10T74/20—Control lever and linkage systems
  • Y10T74/20576—Elements
  • Y10T74/20636—Detents

Definitions

• the invention relates to a spring for a watch mechanism or a clock mechanism spring.
• the invention also relates to a clock mechanism, including a calendar mechanism, a correction mechanism or a notching mechanism, comprising such a spring.
• the invention also relates to a watch movement comprising such a spring or such a mechanism.
• the watch mechanisms are generally provided with springs, levers and cams which are provided to cooperate to perform various functions of a watch movement. Energy, taken from the motor or provided by the wearer of the wristwatch, is thus accumulated and returned by the springs so as to guarantee the functions, all in a limited volume.
• the horological designs are thus frequently constrained by the size that leads to spring geometries in which the mechanical stresses are very important compared to the forces to be provided. In some cases, it is possible to implement "son" springs. However, the dimensional tolerances are particularly tight and the bending tolerances are very difficult to guarantee, which makes the industrial and repeatable production of such springs problematic.
• Document EP2309346 discloses a dragging calendar mechanism whose date can be corrected quickly by means of a notching device established by a lever-spring provided to cooperate with a cam. It is specified that this lever-spring is mounted integral with a driving wheel for an axis 28 and a pivot 30. The latter has two distinct pivot points and disposed below the lever. The geometric configuration of this spring is such that it requires to strongly constrain the spring to allow it to deliver a mechanical action of given intensity.
• Document EP0360963A1 discloses a mechanism with two time zones. The setting of a second time zone relative to the reference time zone is also effected by means of a notching device established by a lever-spring provided to cooperate with a cam. This lever-spring is pivotally mounted around two separate axes and disposed below the lever. The geometrical configuration of this spring is such that it requires to strongly constrain the spring to allow it to deliver a mechanical action of given intensity.
• the object of the invention is to provide a clock mechanism spring to overcome the drawbacks mentioned above and improve the known springs of the prior art.
• the invention provides a spring for minimizing the mechanical stresses it undergoes when it is loaded while being able to be housed in a given space.
• the watch mechanism spring comprises a body extending between a first end of the spring and a second end of the spring.
• the spring is intended to be mechanically linked to a frame at each of the first and second ends.
• the spring comprises, between the first and the second end, at least one member intended to act by contact on an element of the watch mechanism.
• the spring comprises a first mechanical connecting element at the frame at the first end and a second mechanical connecting element to the frame at the second end.
• the spring is intended to be linked via a pivot connection to the frame at the first end and the spring is intended to be connected via a pivot connection to the frame at the second end.
• the first mechanical connecting element and the second mechanical connecting element are pivot connecting elements.
• a clock mechanism is defined by claim 1 1.
• a watch movement is defined by claim 14.
• a timepiece is defined by claim 15.
• Figure 1 is a schematic view of a timepiece comprising a first variant of a watch spring according to the invention occupying a first configuration.
• Figure 2 is a view of the first variant of the watch spring according to the invention occupying a second configuration.
• Figure 3 is a view of a second variant of a watch spring according to the invention occupying a first configuration.
• Figure 4 is a view of the second variant of the watch spring according to the invention occupying a second configuration.
• FIG. 5 is a graph illustrating two characteristics torque (C) - angular displacement ( ⁇ ) of the first and second variants of the spring according to the invention, the same coefficient of friction existing between each spring and the parts on which it is mounted. The maximum stresses within these springs, for a given material, are also annotated for each of their extreme position.
• Figure 6 is a view of a calendar mechanism equipped with a third variant of a watch spring according to the invention.
• Figure 7 is a view of the third variant of the watch spring according to the invention.
• Figure 8 is a view of a fourth variant of a watch spring according to the invention.
• a timepiece 300 according to the invention is described below with reference to FIG.
• the timepiece is for example a watch, including a wristwatch.
• the timepiece comprises a watch movement 200, in particular a watch movement of the mechanical type.
• the watch movement comprises a mechanism 100, in particular a mechanism including an element 19 and a spring 10.
• a first variant of the spring 10 for a clock mechanism or a clock mechanism spring is described hereinafter with reference to FIGS. 2.
• the spring is for example used in a watch mechanism of the rapid correction device type of a time indication.
• the spring 10 is for example provided to cooperate by contact action on an element 19 of the clock mechanism to generate a detent during the correction so as to allow the adjustment of a time indication by a predefined angular pitch.
• the spring is intended to be mounted on a frame.
• the spring 10 comprises a body January 1 which extends between a first end 12 of the spring and a second end 13 of the spring.
• the body 1 1 of the spring 10 has a zone 14 of substantially rectangular section strongly deformable under an action of a given intensity. This zone is located between the points 12a and 13a of the respective ends 12 and 13 beyond which the section of the body 1 1 of the spring 10 can vary substantially.
• the zone 14 does not generally comprise the connecting elements 15 and 16 of the respective ends 12 and 13.
• the curve 18 along which the zone 14 of the body 11 extends between the points 12a and 13a is preferably a circular curve or substantially circular inside which is the center of gravity 1 1 g of the body 1 1 of the spring.
• This curve is generally concave seen from the center of gravity 1 1 g of the body 1 1 of the spring. However, the curve may locally present one or more convexities.
• Curve 18 is also preferably a planar curve.
• the body of the spring or the spring extends in a plane.
• the first end of the spring can be oriented in a first plane and the second end can be oriented in a second plane.
• the foreground and the second shot are not necessarily parallel.
• the axis of a first connecting element is perpendicular to the first plane and the axis of a second connecting element is perpendicular to the second plane.
• the first connecting element provided on the spring cooperates with another connecting element on the frame to form a pivot connection between the spring and the frame.
• second connecting element provided on the spring cooperates with another connecting element on the frame to form a pivot connection between the spring and the frame.
• the spring comprises, between the first 12 and the second end 13, a member 17 intended to act by contact on the element 19 of the watch mechanism which is preferably movable relative to the frame.
• the element 19 is for example a star 19 rotatable about its center
• the member 17 is for example a finger 17 projecting on the body 1 1 of the spring. This finger comprises a contact surface intended to act by contact on the star 19.
• the member 17 is oriented towards the inside of the curve of the body of the spring seen from the center of gravity of the body of the spring.
• the spring is intended to be mechanically linked to a frame at each of the first and second ends by the first and second pivot links, respectively. More particularly, the spring comprises a first pivot connecting element to the frame at the first end 12 and a second pivot connecting member 16 to the frame at the second end 13.
• the first connecting element preferably comprises a bore Or a bore portion for receiving an axis mounted on the frame.
• the second connecting member preferably comprises a bore or a bore portion 16 for receiving an axis mounted on the frame.
• a connecting element comprises a bore portion
• the spring can be engaged on an axis fixed to the frame.
• the distance D between the first and second ends, in particular between the axis of the first connecting element and the axis of the second connecting element is of the order of 2 mm and the thickness E measured at the ends 12 and 13 is of the order of 0.2 mm.
• the thickness E of the spring is measured perpendicularly to the plane of FIGS. 1 and 2.
• the angle ⁇ formed by the two half-lines originating in the center of gravity 1 1 g of the body 1 1 of the spring and passing through the axis the first connecting element 15 and the axis of the second connecting element 16 is of the order of 60 °.
• the star When turning the star of the configuration of Figure 1 to that of Figure 2, the star acts by contact on the finger 17 of the spring. There is an elastic deformation of the spring which stores mechanical energy. There are also rotations at the ends of the spring. Conversely, when the star of the configuration of FIG. 2 continues to rotate with that of FIG. 1, it is the finger 17 which acts by contact on the star 19. The spring then restores the energy that he had stored, and rotations occur at the ends of the spring.
• the spring is intended to store mechanical energy because of its deformation under the effect of a motor member or the user and to restore this energy or a portion of this energy to the element 19, in particular by the contact of the member 17 on the element 19. This energy return allows to drive or to activate or actuate the element or mechanism.
• the restored energy takes the form of a mechanical work actuating or setting in motion or moving the element 19.
• the spring can be mounted prestressed on the frame in a configuration where it does not act on the element 19 or in a configuration where the intensity of its contact action on the element 19 is minimal.
• the angular rigidity of the spring is optimized so that the spring produces a range of torque or force adapted for example to the notching function as described. previously, and that the mechanical stresses therein are lower than the maximum allowable stress of the material constituting the spring.
• the two pivot connections of the spring make it possible to minimize the mechanical stresses that the spring undergoes when it is stressed.
• Such a spring is particularly advantageous in view of the small size it requires. Moreover, such a spring is also particularly suitable for industrial production. More particularly, by the two pivot links of the spring, the angular stiffness of the spring is optimized so that the zone 14 of the body 1 1 of the spring 10 has a section adapted to an industrial manufacturing process.
• the distance D between the first and second ends, in particular between the axis of the first connecting element and the axis of the second link element can be minimized.
• the distance D may in particular be reduced to the minimum distance required between the axis of the first connecting element and the axis of the second connecting element facing the thickness E of the spring and the residual material walls measured at its two ends.
• Figures 3 and 4 illustrate a second variant of a spring 20 which may, for example, have the same functions as the spring 10 described above.
• the spring 20 is also used in a rapid correction device for a time indication.
• the spring 20 is for example designed to cooperate by contact action on a star 29 of a mechanism watchmaker, identical to the star 19, to generate a notch during the correction so as to allow the adjustment of a time indication by a predefined angular step.
• the star acts by contact on the finger 27 of the spring.
• There is an elastic deformation of the spring which stores mechanical energy.
• the star of the configuration of FIG. 4 continues to rotate with that of FIG. 3, it is the finger 27 that acts by contact on the star 29.
• the spring restores the energy that he had stored, and rotations occur at the ends of the spring.
• the spring 20 once mounted on the frame, the distance D between the first and second ends, in particular between the axis of the first connecting element and the axis of the second connecting element, is order of 1 mm and the thickness E measured at the ends 22 and 23 is of the order of 0.2 mm within the spring 20 illustrated in Figures 3 and 4.
• the thickness E of the spring is measured perpendicularly to the plane of the figures 3 and 4.
• the curve 28, seen from the center of gravity 21 g of the body 21 of the spring, extends over an arc a of the order of 210 ° within the spring 20 illustrated in the configuration of FIG.
• angle ⁇ formed by the two half-lines originating from the center of gravity 21 g of the body 21 of the spring and passing respectively through the ends 22 and 23, in particular by the axis of the first connecting element 25 and the axis of the second connecting element 26 is of the order of 45 ° within the illustrated spring 10 in the configuration of Figure 3.
• Simulations making it possible to establish the torque characteristic C - angular displacement ⁇ of the spring 10 and the spring 20, and making it possible to evaluate the stresses ⁇ within these springs have been realized.
• the results shown in FIG. 5 show the influence of the distance D on the torques and mechanical stresses of the springs 10 and 20. For a given coefficient of friction as well as a given material such as a spring steel, a constraint is computed.
• the element 19, 29 moves at least 10 °, or even at least 15 °, or even at least 20 °, or even at least 30 °, relative to the constructed during a transition from a configuration of maximum stress in the spring to a configuration of minimum stress in the spring.
• This displacement takes place under the effect of the return of the mechanical energy stored in the spring, especially in the form of mechanical work.
• the finger 17, 27 can move by at least 5 °, or even at least 10 °, about the axis of a connecting element 25.
• a third embodiment of a spring 30 for a watch mechanism is described below with reference to FIGS. 6 and 7.
• the spring 30 is for example used in a calendar device shown in FIG. 6.
• the spring 30 is example provided for cooperating by contact action on an element 1 of the calendar device to generate a drive of a day display disk (not shown in Figure 6). It allows to advantageously replace a conventional drive finger associated with an additional spring may clog too heavily the clock mechanism.
• the third variant of the spring differs from the first variant only by the elements which are described below.
• the spring 30 comprises a body 31 which extends between a first end 32 of the spring and a second end 33 of the spring.
• the spring comprises, between the first and the second end, a member 37, in particular a driving finger 37, intended to act by contact on the element 1 of the watch mechanism.
• the body 31 of the spring has a zone 34 of substantially rectangular section which is highly deformable under an action of a given intensity. This zone is located between the points 32a and 33a of the respective ends 32 and 33 beyond which the section of the body 31 of the spring 30 can vary substantially.
• the zone 34 does not generally comprise the connecting elements 35 and 36 of the respective ends 32 and 33.
• the curve 38 along which the zone 34 of the body 31 extends between the points 32a and 33a is preferably a circular curve or substantially circular inside which is the center of gravity 31 g of the body 31 of the spring.
• This curve is generally concave seen from the center of gravity 31 g of the body 31 of the spring.
• This curve is generally concave seen from the center of gravity 31 g of the body 31 of the spring.
• the curve may locally present one or more convexities.
• Curve 38 is also preferably a planar curve.
• the body of the spring or the spring extends according to a plane.
• the first end of the spring can be oriented in a first plane and the second end can be oriented in a second plane.
• the foreground and the second shot are not necessarily parallel.
• the axis of the first connecting element is perpendicular to the first plane and the axis of the second connecting element is perpendicular to the second plane.
• the member 37 is oriented outwardly of the curve of the spring body seen from the center of gravity of the spring body.
• the spring is intended to be mechanically linked to a frame at each of the first and second ends by the first and second pivot links, respectively. More particularly, the spring comprises a first pivot connecting element to the frame at the first end 32 and a second connecting element 36 pivoting to the frame at the second end 33.
• the first connecting element preferably comprises a bore Or a bore portion for receiving an axis mounted on the frame.
• the second connecting element preferably comprises a bore or a bore portion 36 for receiving an axis mounted on the frame.
• a connecting element comprises a bore portion
• the spring can be engaged on an axis fixed to the frame.
• Figure 7 illustrates a spring 30, in a given configuration, which has the characteristics mentioned below.
• the distance D between the first and second ends, in particular between the axis of the first connecting element 35 and the axis of the second connecting element 36 is minimized and is of the order of 1 mm.
• the thickness E measured at the ends 32 and 33, and measured perpendicular to the plane of FIG. 7, is of the order of 0.2 mm.
• the angle on which the curve 38 extends is of the order of 215 °.
• the angle ⁇ formed by the two half-lines originating in the center of gravity 31 g of the body 31 of the spring and passing through the axis of the first connecting element 35 and the axis of the second connecting element 36 is the order of 30 °.
• the frame 3 is for example constituted by a wheel 3.
• the element 1 is movable relative to the frame 3.
• the element is a star of the days moving in rotation around its center with respect to a structure on which is also rotatably mounted the wheel 3.
• Star 1 comprises seven teeth 1a and carries the day display disc (not shown in FIG. 6).
• the toothing 1 of this star 1 is indexed angularly through a spout 2 and is driven instantaneously, every 24 hours at the time of midnight, through the drive wheel 3.
• This device is accompanied a fast correction mechanism consisting of a corrector 4 and a correction wheel 4 'integral with the star 1.
• the corrector 4 When this mechanism is activated, the corrector 4 is positioned so that its toothing can mesh in one direction the toothing of the correction wheel 4 '.
• the indication of the days is corrected only in chronological sense.
• FIG. 6 illustrates this timing mechanism in a configuration in which the driving finger 37 is positioned and held within the toothing 1a by means of a rocker 8, a roller 8a of which is applied against a stop curve 6c of a cam 6. More particularly, FIG. 6 illustrates the finger 37 in a position in which it must be able to retract over an entire angular step of the star 1, ie about 50 °, during a rapid correction of the indication of days.
• the retractable finger must be able to support a rotation around the first mechanical connecting element 35 over a large angular extent of the order of 50 °, while having constraints within it lower than those which are admissible by the material constituting it.
• the spring 30 plates the finger 37 against a pin 40 so that the finger 37 behaves like a rigid finger to ensure the jump of the indication of the days.
• the spring is slightly pre-armed during assembly.
• the spring is shown after mounting, in particular by plugging the second end on an axis 36 '.
• the torque produced by the spring also allows the finger 37 to stop the star of days after the date jump, and thus avoids any risk of double jump.
• the finger 37 pivots a value of about 50 ° around the pivot around the pin 35 '.
• the other pivot, around the pin 39 allows him to generate such a movement of the finger 37 while limiting the deformation of the spring.
• the constraints, during complete retraction of the finger 37 thus remain below the elastic limit of the spring material.
• the angular rigidity of the spring is optimized so that the movement of the finger 37 is maximized.
• the two pivot connections of the spring make it possible to minimize the mechanical stresses that the spring undergoes when it is stressed. These constraints are all minimized as the distance between the two pivot links of the spring is minimized.
• the member 37 is preferably close to one of the two ends 32 and 33 of the spring so as to define a continuous deformable zone 34 whose extent is maximized between the points 32a and 32b of the spring.
• the position of the element on which the spring acts and the position of at least one of the two ends of the spring are fixed, it may be advantageous to interrupt the deformable zone of the spring by the rigid member capable of coming into contact with the element on which the spring acts.
• this configuration can be quite satisfactory for minimizing the stresses within the spring in a given configuration.
• FIG. 8 illustrates a fourth variant embodiment of a spring 50 which may, for example, have the same functions as the spring 30 described above.
• the spring 50 comprises, between the first and the second end, a member 57 intended to act by contact on an element of a watch mechanism.
• the body 51 of the spring has a zone 54 of substantially rectangular section strongly deformable under an action of a given intensity.
• This zone 54 consists of two parts which are delimited by the member 57.
• This zone is located between the points 52a and 53a of the respective ends 52 and 53 beyond which the section of the body 51 of the spring 50 can vary substantially.
• the curve 58 along which extends the zone 54 of the body 51 between the points 52a and 53a is preferably a circular curve 58 or substantially circular inside which is the center of gravity 51 g of the body 51 of the spring. This curve is generally concave seen from the center of gravity 51 g of the body 51 of the spring.
• Figure 8 illustrates a spring 50, in a given configuration, which has the characteristics mentioned below.
• the distance D between the first and second ends, in particular between the axis of the first connecting element 65 and the axis of the second connecting element 66 is of the order of 1 mm.
• the thickness E measured at the ends 62 and 63, and measured perpendicular to the plane of FIG. 8, is of the order of 0.2 mm.
• the angle at which the curve 68 extends is of the order of 265 °.
• the angle ⁇ formed by the two half-lines originating from the center of gravity 61 g of the body 61 of the spring and passing through the axis of the first connecting element 65 and the axis of the second connecting element 66, is the order of 25 °.
• the proximity of the centers of the mechanical connection elements allows a low angular rigidity, allows to perform a large angular stroke without exceeding the allowable stress.
• the distance between the first and second ends, in particular between the axis of the first connecting element and the axis of the second connecting element is preferably less than 5 mm, or even less than 2 mm. , or less than 1 mm, and / or less than 8 times the thickness of the ends of the spring, or even less than 6 times the thickness of the ends of the spring.
• the spring comprises, between the first and the second end, at least one member intended to act by contact on an element of the watch mechanism.
• the spring generally has an annular shape having an opening.
• the curve 18, 28, 38, 58 is preferably a flat curve.
• the body of the spring or the spring extends in a plane.
• the first end of the spring can be oriented in a first plane and the second end can be oriented in a second plane.
• the foreground and the second shot are not necessarily parallel.
• the axis of the first connecting element is perpendicular to the first plane and the axis of the second connecting element is perpendicular to the second plane.
• the curve 18, 28, 38, 58 according to which extends the zone 14, 24, 34, 54 of the body 1 1, 21, 31, 51 between the points 12a, 22a, 32a , 52a and 13a, 23a, 33a, 53a is preferably a circular or substantially circular curve within which is the center of gravity 1 1 g, 31 g, 51 g of the body 1 1, 31, 51 spring .
• This curve is generally concave seen from the center of gravity 11 g, 21 g, 31 g, 51 g of the body 1 1, 21, 31, 51 of the spring.
• the curve may locally present one or more convexities.
• this curve seen from the center of gravity of the body of the spring, extends over an arc of an angular range a greater than 200 ° or 220 °.
• the centers of gravity 1 1 g, 21 g, 31 g, 51 g of the bodies of the springs 10, 20, 30, 50 can be the centers of gravity of the curves passing through the centers of the straight sections of the springs and connecting the axes connecting elements.
• the spring can be made of different materials. It may in particular be made of spring steel, silicon, nickel, nickel-phosphorus or amorphous metal alloy.
• the spring can be made for example by a mechanical process such as stamping or wire cutting.
• the spring can also be made by stereolithography, by a LIGA process, by a DRIE etching process, or by a laser etching process. These production methods make it possible in particular to produce small thicknesses of material at the level of the connecting elements, which allows closer to the axes of the mechanical connection elements.
• the member intended to act by contact on an element of the watch mechanism may have a thickness different from that of the other parts of the spring.
• the spring according to the invention may have zones of different thicknesses.
• the monobloc spring maximizes the energy accumulated during its charging while limiting the stresses within it.
• the spring provides the forces necessary to perform various horological functions in a given volume. To do this, the one-piece spring has two distinct and close pivots.
• the spring optimally.
• the distance between the axes of the connecting elements directly depends on the minimum thicknesses of material achievable by the production method.
• the invention also relates to a watch movement or a timepiece, in particular a watch, comprising a watch mechanism as described above or a spring as described above.
• the term “spring” has been used to designate a monobloc element comprising a first part highly deformable under an action of a given intensity and a second part, particularly at the level of the organ, weakly deformable, or even deformable under this same action. This was done by analogy with other uses of the term “spring”.
• the term “spring” is also customarily used to designate a helical spring biased in tension and terminated by a hook at each of these ends.
• a coil spring comprises a first portion (helically shaped) strongly deformable under an action of a given intensity and a second portion (the hooks) weakly deformable, or even deformable, under this same action.
• body or “spring body” refers to the spring itself, that is to say the material forming the spring.

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• Physics & Mathematics (AREA)
• General Physics & Mathematics (AREA)
• Engineering & Computer Science (AREA)
• Automation & Control Theory (AREA)
• Springs (AREA)
• Electric Clocks (AREA)
• Coupling Device And Connection With Printed Circuit (AREA)

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• 2012
  • 2012-12-26 JP JP2014549456A patent/JP6148683B2/ja active Active
  • 2012-12-26 WO PCT/EP2012/076911 patent/WO2013102598A2/fr active Application Filing
  • 2012-12-26 EP EP12813874.0A patent/EP2798413B1/de active Active
  • 2012-12-26 US US14/368,745 patent/US9395691B2/en active Active
  • 2012-12-26 CN CN201280065234.3A patent/CN104024961B/zh active Active

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