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EP3619579B1 - Uhrvorrichtung mit positionierorgan - Google Patents

Uhrvorrichtung mit positionierorgan Download PDF

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Publication number
EP3619579B1
EP3619579B1 EP18723605.4A EP18723605A EP3619579B1 EP 3619579 B1 EP3619579 B1 EP 3619579B1 EP 18723605 A EP18723605 A EP 18723605A EP 3619579 B1 EP3619579 B1 EP 3619579B1
Authority
EP
European Patent Office
Prior art keywords
positioning member
elastic
engagement element
timepiece device
support
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.)
Active
Application number
EP18723605.4A
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English (en)
French (fr)
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EP3619579A1 (de
Inventor
Jean-Baptiste LE BRIS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Patek Philippe SA Geneve
Original Assignee
Patek Philippe SA Geneve
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Filing date
Publication date
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Publication of EP3619579A1 publication Critical patent/EP3619579A1/de
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Publication of EP3619579B1 publication Critical patent/EP3619579B1/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
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
    • G04B11/022—Devices allowing the motion of a rotatable part in only one direction with a ratchet which makes contact with the rotating member by means of teeth
    • 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
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
    • G04B11/022—Devices allowing the motion of a rotatable part in only one direction with a ratchet which makes contact with the rotating member by means of teeth
    • G04B11/024—Devices allowing the motion of a rotatable part in only one direction with a ratchet which makes contact with the rotating member by means of teeth rotatable about a fixed axis by means of spring action

Definitions

  • the invention relates to a horological device including a positioning member such as a jumper or a pawl.
  • a jumper is an organ, generally a lever, terminated by two inclined planes which press between the points of two consecutive teeth of a wheel, also called a star, under the action of a spring, to maintain it in a certain angular position. .
  • the teeth raise the jumper which then falls between two other teeth.
  • a jumper allows the wheel to move in both directions.
  • a ratchet is a member, generally a lever, provided with a nose which penetrates into the teeth of a wheel under the action of a spring to maintain it in a certain angular position.
  • the teeth raise the pawl which then falls between two other teeth. In the other direction, the pawl prevents the wheel from turning due to the shape of its nose and / or the toothing of the wheel.
  • the object of the invention is to provide a timepiece device comprising a toothed component and a positioning member, said positioning member ensuring good maintenance in position of the toothed component while attenuating or even eliminating any peak in energy consumption during latching. advancement of said toothed component by one step.
  • the invention proposes a device according to claim 1.
  • the invention also proposes a timepiece such as a wristwatch or a pocket watch comprising such a horological device.
  • a watch device 1 intended to form part of a watch mechanism such as a movement or a mechanism additional to the movement, comprises a wheel 11 comprising a toothing 111, and a control member. positioning 10.
  • the set of teeth 111 is typically a set of teeth comprising truncated teeth.
  • the positioning member 10 shown in figure 1 is a ratchet. It maintains the wheel 11 in position and allows its rotation only in the anti-clockwise direction, as indicated by arrow B.
  • the wheel 11 is typically a toothed wheel carrying, driving or forming a display member, such as a disc, a needle or a display crown.
  • a display member such as a disc, a needle or a display crown.
  • it may also be, for example, a column wheel, a barrel or ring ratchet, a winding wheel, or any type of toothed wheel traditionally positioned by a pawl. It is typically other than an escape wheel.
  • the positioning member 10 comprises an engagement member 15, a support 12 and an elastic member 14 connecting the engagement member 15 to the support 12.
  • the elastic member 14 typically comprises several elastic blades distributed, preferably uniformly , around the support 12. These elastic blades 14 connect the support 12 to the engagement element 15 which is itself engaged in the teeth 111 of the wheel 11 to be positioned.
  • the positioning member 10 shown in figures 1 and 2 further comprises a rim 13 in the form of a closed circle carrying the engagement element 15 and forming the connection between the latter and the elastic member 14.
  • the support 12 is fixed to a fixed or mobile frame 100, on which the wheel 11 is also mounted, said frame 100 typically comprising the plate carrying the watch mechanism.
  • the rim 13 as well as the engagement element 15 which is integral with it are guided in rotation with respect to the support 12 by the elastic blades 14.
  • the engagement element 15 takes the form of a radial projection defining two inclined planes forming an angle of 120 ° between them and preferably pointing towards the center of the wheel 11.
  • the set of elastic blades 14 exerts a return moment tending to cause the rim 13 to pivot around the support 12 in the anti-clockwise direction of the figures 1 and 2 .
  • the rotation of the rim 13 in the anti-clockwise direction is limited by a stop 16, fixed to the frame 100, against which a protuberance 17 of the rim 13 rests, when the device 1 is in the rest position, that is, that is to say when the engagement element 15 is engaged, in a centered manner, in a hollow 11a of the toothing 111, between two consecutive teeth of the wheel 11, as illustrated in figure 1 .
  • the figure 2 represents, for the understanding of the invention, the positioning member 10 isolated, that is to say free from any interaction with the stop 16 or with the wheel 11.
  • the positioning member 10 Due to the shape of its elastic blades 14, the positioning member 10 has a preferred direction of rotation of its rim 13, and therefore of its engagement element 15, relative to its support 12, this direction being defined as that which allows, from a state of rest of said isolated positioning member 10 in which all of its elastic blades 14 are at rest, the greatest relative angular displacement of the engagement element 15 with respect to the support 12.
  • the arrow A shown on figures 1 and 2 illustrates this preferred direction of rotation of the engagement element 15 relative to the support 12; this direction corresponds to the clockwise direction in these figures.
  • ⁇ be the angular position of the engagement element 15 of the isolated positioning member 10 relative to the support 12, ⁇ being equal to zero when the isolated positioning member 10 is at rest, that is to say say when all of its elastic blades 14 are at rest, and increasing with the relative angular displacement of the engagement element 15 with respect to the support 12 in the preferred direction of rotation of the isolated positioning member 10; the figure 3 illustrates the evolution M ( ⁇ ) of the elastic return moment exerted by the assembly of the elastic blades 14 in the isolated positioning member 10 as a function of the angular position ⁇ of the engagement element 15 relative to the support 12 .
  • the positioning member 10 is said to be armed with x °.
  • the isolated positioning member 10 exhibiting a curve M ( ⁇ ) of the type shown in figure 3 differs from classical elastic structures. Its properties are based on a sinuous shape of its elastic blades 14 which deform so as to generate a substantially elastic restoring moment. constant (the curve M ( ⁇ ) has a plateau between ⁇ 1 and ⁇ 2 ) over a predetermined range of angular positions of its engagement element 15 relative to its support 12. Obtaining such elastic blades requires a specific design and parameterized.
  • the topological optimization referred to in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic leaves 14.
  • each of the elastic blades 14 of the positioning member 10 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the positioning member 10 to be designed as well as a constraint “(M max -M min ) / ((M max + M min ) / 2) ⁇ 0.05”.
  • the equation “(M max -M min ) / ((M max + M min ) / 2) ⁇ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range.
  • all of the elastic blades 14 of the positioning member 10 of the device 1 is designed, in particular by virtue of its shape, to exert, in this member 10, a substantially constant elastic restoring moment (constancy of 5%) over a range of angular positions of the rim 13 and of the engagement element 15 which it carries relative to the support 12 of at least 10 °, preferably at least 15 °, more preferably at least 20 °.
  • this positioning member 10 is designed a particular positioning member comprising four elastic blades distributed uniformly around the support 12.
  • the dimensions of this positioning member 10 are as follows: Outside diameter of the rim: 12 mm Support outer diameter: 2 mm Inside diameter of the rim: 10 mm Height: 0.12 mm Thickness of elastic blades : 24 ⁇ m
  • control points Q 0 , Q 1 , Q 2 , Q 3 , Q 4 , Q 5 , Q 6 were used.
  • the coordinates of these control points are shown in Table 1 below.
  • the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bézier curve of order 4 based on control points Q 3 to Q 6 .
  • the graph of the figure 4 shows the geometry of the external diameter of the support 12, of the internal diameter of the rim 13 and of one of the elastic blades 14 of the particular positioning member 10 that the applicant has designed, the geometry of said blade 14 being defined by a curve passing through all the coordinates of points defined in table 2 above.
  • This graph is produced in an orthonormal coordinate system.
  • the figures 5a and 5b represent the results of a simulation of the evolution of the elastic return moment of the particular positioning member 10 thus produced as a function of the angular position ⁇ of its engagement element 15 relative to its support 12.
  • the stiffness of the positioning member 10, more precisely of its set of elastic blades 14, is the derivative of the function M ( ⁇ ) defined above.
  • the stiffness of the isolated positioning member 10 is negative.
  • the stiffness of the isolated positioning member 10 is zero at the point at which the elastic restoring moment reaches a local maximum. In the present invention, one places oneself in this range [ ⁇ a , ⁇ b ] or at least partly in this range.
  • the positioning member 10 is therefore arranged so that, during the rotation of a pitch of the wheel 11 against the return action of the set of elastic blades 14, the element of engagement 15 moves within a range predetermined position with respect to the support 12, this range being included in the range of positions [ ⁇ 1 , ⁇ 2 ] associated with the positioning member 10 and comprising at least part of the range of positions [ ⁇ a , ⁇ b ] in which the stiffness of all the elastic blades 14 is zero or negative.
  • said predetermined range is included in the range [ ⁇ a , ⁇ b ] or constituted by the latter.
  • the set of elastic blades 14 exerts an elastic return moment tending to cause the rim 13 and the engagement element 15 that it carries around the support 12 to pivot in the direction of the reduction of the angle ⁇ (counterclockwise on the figure 1 ).
  • the engagement element 15 is positioned between two successive teeth of the teeth 111 of the wheel 11 to be positioned now. thus the latter in position under the effect of the return moment exerted by the set of elastic blades 14.
  • angle ⁇ arm the dimensions of the positioning member 10, in particular its diameter and the angle between the inclined planes of its engagement element 15, as well as the shape and dimensions of the teeth 111 of the wheel 11, are chosen so that, during the angular displacement of one step of the wheel 11, the engagement element 15 moves angularly with respect to the support 12 in the range of positions [ ⁇ 1 , ⁇ 2 ] and at least partly in the range of positions [ ⁇ a , ⁇ b ].
  • ⁇ arm is therefore between ⁇ 1 and ⁇ 2 and preferably approximately equal to ⁇ a .
  • the choice of the angle ⁇ arm defines the lower limit of the predetermined range of positions in which the engagement element 15 moves during the rotation of a pitch of the wheel 11.
  • the dimensions of the positioning member 10, in particular its diameter and the angle between the inclined planes of its engagement element 15 as well as the shape and dimensions of the teeth 111 of the toothed wheel 11 define, for their part, the upper limit of this range of positions.
  • the figure 6 presents the results of measurements of the moment of force recorded on the wheel 11 of the device 1 as a function of its angular displacement, during a rotation of an angle ⁇ corresponding to a pitch of the wheel 11 in the direction of arrow B .
  • the same toothed wheel 11, 71 was positioned either with the positioning member 10 of the device 1 according to the first embodiment of the invention (curve c 1 ), or with a jumper 70 using a spring 74 with traditional positive stiffness (co curve) as shown in figure 7 .
  • the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises an engagement element 75 engaged in the teeth 711 of a toothed wheel 71.
  • This jumper 70 allows the rotation of the toothed wheel 71 in the two directions (clockwise and anti-clockwise corresponding respectively to arrows G and F of the figure 7 ), however only counterclockwise rotation (arrow F) has been studied here.
  • the angle ⁇ increases with the rotation of the wheel 11 (curve c 1 ) or 71 (curve co) respectively in the direction of arrow B ( figure 1 ) or the arrow F ( figure 7 ).
  • the moment necessary to initiate the rotation of the wheel 11 or “starting moment” is approximately identical in the device 1 using the positioning member 10 and in the device 7 using the traditional jumper 70. It is approximately 0.084 N.mm.
  • the wheel 11 is therefore held in position by the pawl consisting of the positioning member 10 according to the first embodiment of the invention as well as by the traditional jumper 70.
  • the moment necessary to rotate the wheel 11 by one step in the case of the device 1 does not include any operating peak .
  • the horological device 1 comprising a wheel 11 and a positioning member 10 according to the first embodiment of the invention therefore allows a reduction in the maximum instantaneous energy consumption required during the rotation of one step of the wheel to be positioned. compared to a traditional jumper 70 using a spring 74 with positive stiffness allowing an equivalent position to be maintained.
  • Such a horological device 1 also has the advantage of being less sensitive to linear shocks than jumpers or pawls according to the prior art. This is due to the good balancing of its positioning member 10. This reduction in sensitivity to linear shocks can make it possible to lower the value of the starting moment while maintaining good support in the event of linear shocks and thus to reduce overall consumption. energy during a one-pitch rotation of the toothed wheel 11.
  • the positioning member 10 of the device 1 according to the first embodiment of the invention is typically monolithic. It can for example be manufactured by machining, in particular in the case where it is made of metal or of an alloy such as Nivaflex®, by DRIE etching in the case of silicon for example, or also by molding, cutting, machining, especially in the case where it is made of plastic or metallic glass.
  • the positioning member 10 may only comprise a single elastic blade 14.
  • the rim 13 may also be interrupted and take the form of an arc of a circle, as illustrated in FIG. figure 8 .
  • the very structure of the positioning member 10 involves the centering of the support 12 relative to its rim 13. However, it may include a centering device aimed at reinforcing the centering of the support 12.
  • a centering device typically comprises a rigid element of junction 18, on the one hand, fixed integrally to at least one zone of the rim 13 and on the other hand, positioned freely in rotation about an axis 19, said axis 19 being integral with the support 12 and centered on this support 12 .
  • the figures 10a and 10b are views respectively from below and from above of a positioning member 10 equipped with such a centering device.
  • the positioning member 10 illustrated in figure 8 also includes such a centering device.
  • the horological device 1 may comprise a positioning member of a different shape from that illustrated in figures 1 and 2 , it can typically include elastic strips of a different shape from that illustrated in figure 4 . It can in particular take a form such as shown in figure 9 .
  • the positioning member 20 shown in figure 9 comprises a support 22 and a rim 23 connected by elastic blades 24, the rim 23 carrying an engagement element 25 intended to be engaged in the teeth of a toothed component to be positioned and held in this teeth under the effect of the moment return exerted by all the elastic blades 24.
  • a horological device 3 according to a second embodiment of the invention comprises a wheel 31 comprising a toothing 311, and a positioning member 30.
  • the positioning member 30 is here a jumper. It maintains the wheel 31 in position and allows it to rotate in both directions, clockwise and anti-clockwise, as indicated respectively by arrows C and D on the left. figure 11 .
  • the wheel 31 is typically a toothed wheel carrying, driving or forming a display member such as a disk, a needle or a display crown. As a variant, it may also be, for example, a column wheel or any type of toothed wheel traditionally positioned by a jumper. It is typically other than an escape wheel.
  • the positioning member 30 comprises a rigid mobile element 33 and an elastic member 34 connecting the latter to a rigid support 32.
  • the elastic member 34 typically comprises a pair of parallel elastic blades working in buckling. Each of these blades 34 is interrupted in its central part by the rigid element 33 and has its two ends joined to said rigid support 32.
  • the support 32 is fixed to a frame 300 on which the wheel 31 is also mounted and the rigid element 33 is movable relative to this support 32.
  • the frame 300 can be fixed or movable and typically comprises the plate carrying the mechanism or movement. watchmaker of which the device is part 3.
  • the rigid element 33 is guided in translation by the elastic blades 34 and moves along a straight line (d) preferably passing through the center of the wheel 31. It comprises an engagement element 35 engaged in the teeth 311. of the wheel 31 to be positioned.
  • the engagement element 35 takes the form of a projection defining two inclined planes forming an angle of 120 ° between them and preferably pointing towards the center of the wheel 31.
  • the engagement element 35 moves with the rest of the rigid element 33 along the line (d) defined above.
  • the straight line (d) passes through the center of the wheel 31 and the assembly comprising the elastic blades 34 and the rigid element 33 is symmetrical with respect to this straight line (d).
  • the pair of blades 34 is pre-armed and exerts a force tending to push the engagement element 35 against the wheel 31, as shown by the arrow E at the bottom. figure 11 .
  • the elastic blades 34 are here preformed flamed, that is to say they are machined with a flamed shape. They could however be preformed straight and work in buckling under the effect of compression of their ends. To do this, the support 32 could be split in its central part to define two parts movable with respect to one another allowing adjustment of the compression. Each of them could also be preformed in the form of two V-shaped half-lines, and only buckle under the effect of its pre-winding.
  • the movement of the engagement element 35 in the direction opposite to the arrow E can be limited by a stop 36 forming part of the support 32.
  • the figure 12 represents, for the understanding of the invention, the isolated positioning member 30.
  • the positioning member 30 is therefore considered here without the stop 36 and outside the device 3, that is to say free from any interaction with the toothed wheel 31.
  • This force was measured, for each position ⁇ , by measuring the opposite force required to maintain the engagement element 35 in a given position.
  • the positioning member 30 is said to be armed with x mm.
  • the isolated positioning member 30 exhibiting an evolution of the force F ( ⁇ ) of the type shown in figure 13 differs from classical elastic structures. Its properties are based on the capacity of its elastic blades 34 to work in buckling, which allows it to behave like a bistable.
  • the Applicant has designed a particular positioning member 30 comprising a pair of elastic blades 34 parallel.
  • the dimensions of this positioning member 30 are those indicated in Table 1 below: Table 1: Dimensions Unit Value Arrow (f) of blades 34 at rest [mm] 0.3 Blade length (L) 34 [mm] 12.5 Slat thickness (e) 34 [mm] 0.12 Height of slats 34 [ ⁇ m] 35 Angle of the inclined planes defining the engagement element 35 [°] 120 ° Jump back of the jumper during the rotation of one step of the wheel 31 [mm] 0.3
  • the figure 13 shows an analytical model representing the evolution of the force F ( ⁇ ) of the particular positioning member 30 thus produced as a function of the position of its engagement element 35 along the line (d).
  • This model considers a monolithic positioning member made of an alloy based on cobalt, nickel and chromium, more precisely in Nivaflex® 45/18, but any suitable material can be used.
  • materials such as silicon typically coated with silicon oxide, metallic glasses, mineral glasses, ceramic glasses, plastics or CK101 (unalloyed structural steel) are also suitable. It is however conceivable to produce a non-monolithic positioning member 30 by assembling several elements or parts, these elements can moreover be made of identical materials or different from each other.
  • the stiffness of the positioning member 30 is the derivative of the function F ( ⁇ ) defined above.
  • the stiffness of the isolated positioning member 30 is negative.
  • the positioning member 30 is therefore arranged to force, during the rotation of a pitch of the wheel 31 against the return action of the pair of elastic blades 34, the engagement element 35 to remain within a predetermined range of positions included in the range of positions [ ⁇ 1 , ⁇ 2 ] associated with the positioning member 30.
  • the positioning member 30 is fixed by its support 32 on the frame 300 of the mechanism so that the tip of the engagement element 35 is engaged centrally between two consecutive teeth of the toothing 311 of the wheel 31 to be positioned, maintaining the latter in position under the effect of the return force exerted by the pair of elastic blades 34, the positioning member 30 being armed with a value ⁇ arm in this position.
  • the choice of the value ⁇ arm defines the lower bound of the predetermined range of positions in which the engagement element 35 moves during the rotation. a pitch of the wheel 31.
  • the shape and dimensions of the teeth of the toothing 311 and the angle between the inclined planes defining the engagement element 35 are chosen so that the maximum value ⁇ reached during the rotation d 'a pitch of the wheel 31 is less than or equal to ⁇ 2 .
  • the stopper 36 prevents movement of the engagement element 35 in the range of positions in which ⁇ is greater than ⁇ 2 . This is a safety aiming to prevent the positioning member 30 from tilting towards the stable state corresponding to the position ⁇ s2 of the engagement element 35 in the event of impact or manipulation affecting the device 3.
  • the figure 14 presents the results of measurements of the moment of force recorded on the wheel 31 of the device 3 as a function of its angular position ⁇ , for a rotation of the wheel 31 by an angle ⁇ corresponding to a step in the direction of arrow D of the figure 11 .
  • the same wheel 31, 71 was positioned either with the positioning member 30 of the device 3 according to the second embodiment of the invention (curve c 2 ), or with the jumper 70 using a spring 74 to traditional positive stiffness (co curve) as shown in figure 7 .
  • the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises an engagement element 75 engaged in the teeth 711 of a wheel 71.
  • This jumper 70 allows the rotation of the wheel 71 in both directions (clockwise and anti-clockwise), however only anti-clockwise rotation (arrow F) has been studied here.
  • the angle ⁇ increases with the rotation of the wheel 31 (curve c 2 ) or 71 (curve co) respectively in the direction of arrow D ( figure 11 ) or the arrow F ( figure 7 ).
  • the moment necessary to initiate the rotation of the wheel 31 or "starting moment" is approximately the same in the case of the use of the positioning member 30 (0.083 N.mm) and in the case of the use of the jumper 70 using a spring 74 with traditional positive stiffness (0.084 N.mm).
  • the wheel 31 is therefore held in position by the jumper using the positioning member 30 according to the second embodiment of the invention as well as by the jumper 70 of the prior art.
  • the moment required to rotate the wheel 31 of a not in the case of the positioning member 30 does not, for its part, include any operating peak. On the contrary, it constantly decreases until it reaches an almost zero value, corresponding to the moment necessary to rotate the wheel 31 when the engagement element 35 is opposite the truncated portion 31b of the toothing 311.
  • the figure 14 therefore shows that both the jumper according to the second embodiment of the invention shown in figure 11 that the jumper 70 according to the prior art allow the repositioning of the toothed wheel 31, 71 to be positioned.
  • the horological device 3 comprising a wheel 31 and a positioning member 30 according to the second embodiment of the invention allows a reduction in the maximum instantaneous consumption of energy required during the rotation of one step of the wheel to be positioned by compared to a traditional jumper 70 using a spring 74 with positive stiffness allowing an equivalent position to be maintained.
  • the energy consumption is less in the case of the use of the positioning member 30 than in the case of the use.
  • the watch device 3 studied therefore makes it possible to reduce the overall consumption of energy during a rotation of one pitch of the toothed wheel 31.
  • Such a watch device 3 also has the advantage of being less sensitive to linear shocks than jumpers or pawls according to the prior art. This is due to the low weight of the movable parts of its positioning member 30, which are the elastic blades 34 and the engagement element 35. This low sensitivity to linear shocks can make it possible to lower the value of the starting moment while maintaining good support in the event of linear shocks and thus further reduce the overall energy consumption during a rotation of one pitch of the toothed wheel 31.
  • the low height of the blades 34 also makes it possible to reduce the height of the device 3. It is thus possible to reduce the height of the timepieces comprising such devices.
  • the positioning member 30 of the device 3 according to the second embodiment of the invention is typically monolithic. It can typically be manufactured by the same methods as those described for the positioning member 10 of the device 1 according to the first embodiment of the invention.
  • the positioning member 30 being a jumper
  • the rotation of the wheel 31 is authorized in both directions, namely, in the direction of arrow D but also in the direction of arrow C ( figure 11 ) and the curve representing the moment of force recorded on the wheel 31 to be positioned as a function of its angular displacement in the direction opposite to that studied would be identical to the curve c 2 .
  • the horological device 3 may comprise a positioning member of a different shape from that illustrated in figures 11 and 12 . It can in particular take a form such as shown in figure 15 , to the figure 17 , to the figure 19a , to the figure 20 , to the figure 21 , to the figure 22 , to the figure 23 , to the figure 24 or at the figure 25 .
  • the figures 16 and 18 represent, respectively by the curves c 3 and c 4 the moment of force necessary to rotate a toothed wheel such as the wheel 31 positioned with a positioning member respectively as shown in figures 15 and 17 during the rotation of one step of this wheel 31, as for the figure 14 .
  • Each of these figures also represents the curve co of the figure 14 for comparison.
  • the positioning member 40 shown in figure 15 differs from the positioning member 30 shown in figure 12 in that its engagement element 45 is truncated. This makes it possible to reduce the recoil of the engagement element 45 during the rotation of one pitch of the wheel 31 to be positioned.
  • Elements 42, 43, 44 of the variant shown in figure 15 correspond respectively to elements 32, 33, 34 of the variant shown in figure 12 .
  • the positioning member 50 shown in figure 17 differs from the positioning member 30 shown in figure 12 in that it also has blades 59 working in flexion. This makes it possible to improve the repositioning of the wheel 31 by the positioning member 30 at the end of a step.
  • the elements 52, 53, 54, 55 of the variant shown in figure 17 correspond respectively to elements 32, 33, 34, 35 of the variant shown in figure 12 .
  • the positioning member 90 shown in figure 21 differs from the positioning member 30 shown in figure 12 in that it has a single elastic blade 94 working in buckling to replace the pair of elastic blades 34.
  • the elements 92, 93, 95 of the variant shown in figure 21 correspond respectively to elements 32, 33, 35 of the variant shown in figure 12 .
  • the rigid element 93 can optionally be guided along the straight line (d) defined above by means of a guide system including for example a finger and a groove. In the absence of such a guide system, the elastic blade 94 of the positioning member 90 does not behave like a bistable but however, has a negative stiffness over a predetermined range of positions of the engagement member 95.
  • the positioning member 110 shown in figure 22 differs from the positioning member 90 shown in figure 21 in that its rigid element 113 and therefore its engagement element 115 interrupt the elastic blade 114 outside its central part, in this case approximately at 3/8 of the length of said blade 114.
  • the eccentricity of the rigid element 113 on the elastic blade 114 decreases the intensity of the force generated by the elastic member comprising this blade 114, however the elastic member maintains a negative stiffness over a predetermined range of positions of the engagement element 115 by compared to support 112.
  • the positioning member 120 shown in figure 23 is a variant of the intermediate positioning member between that shown in figure 12 and the one shown in figure 21 .
  • the positioning member 120 according to this variant comprises an elastic member comprising on one side of its rigid element 123 a half-blade 124a and on the other side of its rigid element 123 a pair of half-blades 124b.
  • the elements 122, 123, 125 of the variant shown in FIG. 120 correspond respectively to elements 32, 33, 35 of the variant shown in figure 12 .
  • the positioning member 130 shown in figure 24 differs from the positioning member 90 shown in figure 21 in that its elastic blade 134 comprises on either side of its rigid element 133, more precisely at the level of each of the junctions of its elastic blade 134 with the support 132, an articulation 136, typically elastic, increasing the flexibility of the blade 134 at said junctions. This has the consequence of reducing the intensity of the force generated by the elastic member comprising this blade 134, however, the elastic member maintains a negative stiffness over a predetermined range of positions of the engagement member 135 with respect to the support 132.
  • the elements 132, 133, 135 of the variant shown in figure 24 correspond respectively to elements 92, 93, 95 of the variant shown in figure 21 .
  • such a positioning member 130 may comprise only a single articulation 136, at the level of only one of the junctions of its elastic blade 134 with its support 132.
  • the positioning member 140 illustrated on figure 25 differs from the positioning member 90 shown in figure 21 in that it is not monolithic but obtained by assembling two parts, each of these parts defining a part 142a, 142b of the support 142, a half-blade 144a, 144b and a part 143a, 143b of the rigid element 143 comprising the engagement element 145.
  • This variant makes it possible to increase the height of the rigid element 143 without modifying the height of the elastic member 144.
  • the positioning member 60 shown in figure 19a differs from the positioning member 90 shown in figure 21 in that its rigid element 63 and in particular its engagement element 65 are not symmetrical.
  • the engagement element 65 defines two inclined planes forming an angle of 145 ° between them, a first plane forming an angle of 60 ° with the line (d) and a second plane forming an angle of 85 ° with the line (d ), as shown in figure 19b .
  • the difference in slope of the inclined planes makes it possible to have a low starting moment with the slope of 85 ° and therefore a low consumption of energy to initiate the rotation of the wheel 31. In addition, this makes it possible to limit the force. tangential on the saltire.
  • the 60 ° slope allows a good repositioning of the wheel.
  • Elements 62 and 64 of the variant shown in figure 19a correspond respectively to elements 92 and 94 of the variant shown in figure 21 .
  • the positioning member 80 shown in figure 20 differs from the positioning member 30 shown in figure 12 in that it comprises a pair of elastic half-blades 84 replacing the pair of elastic blades 34.
  • the elements 82 and 83 of the variant shown in figure 20 correspond respectively to elements 32 and 33 of the variant shown in figure 12 .
  • the rigid element 83 comprises a protuberance 87 bearing against a stop 86.
  • the fact that these elements bear against each other makes it possible to guide the engagement element 85 along the straight line (d ) preferably passing through the center of the wheel 31. It is also possible to envisage an elastic system for guiding in translation which makes it possible to avoid friction between the protuberance 87 of the rigid element 83 and the stop 36.
  • the different variants of the positioning member that can be used in the device 3 according to the second embodiment of the invention make it possible to effectively position the wheel 31 to be positioned with a reduction in the overall energy consumption during the rotation of a pitch of said wheel 31.
  • These different variants also have the same advantages as those associated with the variant presented in figure 11 . They make it possible in particular to eliminate the peak in energy consumption occurring during the rotation of a pitch of the wheel 31 to be positioned with a traditional jumper using a spring with positive stiffness allowing an equivalent position to be maintained.
  • any device according to the invention considered at rest is associated with a moment of force value making it possible to initiate the rotation of the toothed wheel to be positioned.
  • the toothed component is permanently in contact with the positioning member. This gives the device good indexing, positioning and repositioning properties.
  • the toothed wheel with truncated teeth used in the various variants of the invention presented is preferred because it makes it possible to limit the recoil of the engagement element of the positioning member when it rotates by one step. However, it can easily be replaced by a conventional toothed wheel such as a star or by an asymmetric toothed wheel.
  • toothed wheel can also replace the toothed wheel to be positioned of one or the other of the two embodiments described by any other toothed component such as a rack or such as a crown, for example display. , internally toothed.
  • the angle between the two inclined planes defined by the engagement element of the positioning member is typically between 120 ° and 170 ° but may be different.
  • the watch device has the advantage of eliminating the peak in energy consumption observed in the jumpers and pawls traditionally used. It also makes it possible to reduce or even cancel the friction within the positioning member, in particular when it is monolithic, which leads to a reduction in its wear. In addition, such a device makes it possible to reduce the number of components in a mechanism. watchmaker using pawls or jumpers which results in an increase in reliability.
  • the device according to the invention is not very sensitive to linear shocks and advantageously allows a reduction in the overall consumption of energy during the rotation of one pitch of its wheel.
  • the invention also relates to a timepiece such as a wristwatch or a pocket watch comprising such a horological device.

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

Claims (22)

  1. Uhrvorrichtung (1; 3), die ein gezahntes Bauteil (11; 31) und ein Positionierorgan (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) umfasst, wobei das Positionierorgan (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) ein Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145), eine Stütze (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) und ein vorgespanntes elastisches Organ (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) umfasst, das das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) mit der Stütze (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) verbindet, wobei das gezahnte Bauteil (11; 31) verschiedene aufeinanderfolgende Ruhepositionen einnehmen kann, wobei das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) derart gestaltet ist, dass es in jeder der Ruhepositionen zwischen zwei aufeinanderfolgenden Zähnen der Zahnung (111; 311) des gezahnten Bauteils (11; 31) in Eingriff ist und derart durch das elastische Organ (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) zwischen diesen zwei Zähnen gehalten wird, dass es das gezahnte Bauteil (11; 31) in der betrachteten Ruheposition hält, und dass das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) bei einer Verlagerung des gezahnten Bauteils (11; 31) um einen Schritt von einer Ruheposition in die folgende Ruheposition von einem der zwei Zähne gegen die Wirkung des elastischen Organs (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) angehoben wird und sich dann derart zwischen diesem Zahn und einem anderen aufeinanderfolgenden Zahn positioniert, dass es das gezahnte Bauteil (11; 31) in der folgenden Ruheposition hält,
    wobei das Positionierorgan (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) derart gestaltet ist, dass das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) sich bei der Verlagerung des gezahnten Bauteils (11; 31) um einen Schritt in einem vorbestimmten Bereich von Positionen in Bezug auf die Stütze (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) verlagert, dadurch gekennzeichnet, dass die Steifigkeit des elastischen Organs (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) in zumindest einem Teil des vorbestimmten Bereichs gleich null oder negativ ist.
  2. Uhrvorrichtung (1; 3) nach Anspruch 1, dadurch gekennzeichnet, dass die Steifigkeit des elastischen Organs (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) in im Wesentlichen dem gesamten vorbestimmten Bereich gleich null oder negativ ist.
  3. Uhrvorrichtung (1; 3) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Steifigkeit des elastischen Organs (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) in im Wesentlichen dem gesamten vorbestimmten Bereich negativ ist.
  4. Uhrvorrichtung (1; 3) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass das elastische Organ mindestens eine elastische Klinge (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) umfasst, die das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) mit der Stütze (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) verbindet.
  5. Uhrvorrichtung (1; 3) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass das Eingriffselement (15; 25) durch das elastische Organ (14; 24) in Bezug auf die Stütze (12; 22) drehbar geführt wird.
  6. Uhrvorrichtung (1) nach Anspruch 5, dadurch gekennzeichnet, dass das elastische Organ (14; 24) gestaltet ist, um über einen Bereich von Winkelpositionen des Eingriffselements (15; 25) in Bezug auf die Stütze (12; 22) von mindestens 10°, vorzugsweise mindestens 15°, vorzugsweise mindestens 20°, ein im Wesentlichen konstantes elastisches Rückstellmoment auszuüben, wobei der vorbestimmte Bereich sich zumindest teilweise in diesem Bereich befindet.
  7. Uhrvorrichtung (1) nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass das Positionierorgan (10; 20) ferner einen Fußkreis (13; 23) umfasst, der durch das elastische Organ (14; 24) mit der Stütze (12; 22) verbunden ist und das Eingriffselement (15; 25) trägt.
  8. Uhrvorrichtung (1) nach Anspruch 7, dadurch gekennzeichnet, dass der Fußkreis (13; 23) kreisbogenförmig ist.
  9. Uhrvorrichtung (1) nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass sie mindestens eine Vorrichtung (18) zur Zentrierung der Stütze (12; 22) in Bezug auf den Fußkreis (13; 23) umfasst.
  10. Uhrvorrichtung (1) nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, dass sie ferner einen Anschlag (16) umfasst, der typischerweise auf einem Gestell (100) befestigt ist, auf dem die Stütze (12; 22) befestigt ist, wobei der Fußkreis (13; 23) derart gestaltet ist, dass er mit dem Anschlag (16) zusammenwirkt, um das elastische Organ (14; 24) vorzuspannen.
  11. Uhrvorrichtung (1) nach einem der Ansprüche 5 bis 10, wenn der Anspruch 5 von Anspruch 4 abhängig ist, dadurch gekennzeichnet, dass die oder jede der elastischen Klingen (14; 24) eine gewundene Form aufweist.
  12. Uhrvorrichtung (1) nach einem der Ansprüche 5 bis 11, wenn der Anspruch 5 von Anspruch 4 abhängig ist, dadurch gekennzeichnet, dass die geometrische Form des oder der elastischen Klinge (14; 24) eine Bezierkurve oder eine Folge von Bezierkurven ist.
  13. Uhrvorrichtung (3) nach Anspruch 4, dadurch gekennzeichnet, dass das Positionierorgan (30; 40; 50; 60; 80; 90; 110; 120; 130; 140) ein bewegliches starres Element (33; 43; 53; 63; 83; 93; 113; 123; 133; 143) umfasst, das das Eingriffselement (35; 45; 55; 65; 85; 95; 115; 125; 135; 145) definiert, und dadurch, dass die mindestens eine elastische Klinge (34; 44; 54; 64; 84; 94; 114; 124; 134; 144) das starre Element (33; 43; 53; 63; 83; 93; 113; 123; 133; 143) mit der Stütze (32; 42; 52; 62; 82; 92; 112; 122; 132; 142) verbindet und gestaltet ist, um durch Knickung zu wirken.
  14. Uhrvorrichtung (3) nach Anspruch 13, dadurch gekennzeichnet, dass die mindestens eine elastische Klinge mindestens eine geknickte vorgeformte oder V-förmig vorgeformte elastische Klinge (34; 44; 54; 64; 84; 94; 114; 124; 134; 144) umfasst.
  15. Uhrvorrichtung (3) nach Anspruch 13 oder 14, dadurch gekennzeichnet, dass das Positionierorgan (50) ferner mindestens eine Klinge (59) umfasst, die gestaltet ist, um durch Biegung zu wirken, um die Neupositionierung des gezahnten Bauteils (31) durch das Positionierorgan (50) zu verbessern.
  16. Uhrvorrichtung (3) nach einem der Ansprüche 13 bis 15, dadurch gekennzeichnet, dass das starre Element (33; 43; 53; 63; 83; 93) entlang einer Geraden (d) beweglich ist.
  17. Uhrvorrichtung (3) nach Anspruch 16, dadurch gekennzeichnet, dass die Baugruppe, die die elastische Klinge oder elastischen Klingen (34; 44; 54; 94) und das starre Element (33; 43; 53; 93) umfasst, in Bezug auf die Gerade (d) symmetrisch ist.
  18. Uhrvorrichtung (1; 3) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Eingriffselement (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) zwei geneigte Ebenen umfasst, die untereinander einen Winkel bilden, der vorzugsweise zwischen 120° und 170° beträgt und in Richtung der Zahnung (111; 311) zeigt.
  19. Uhrvorrichtung (1; 3) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Zahnung (111; 311) abgestumpfte Zähne umfasst.
  20. Uhrvorrichtung (1; 3) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das gezahnte Bauteil ein Rad (11; 31) ist.
  21. Uhrvorrichtung (1; 3) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Positionierungsorgan (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130) monolithisch ist.
  22. Uhr, die eine Uhrvorrichtung (1; 3) nach einem der vorhergehenden Ansprüche umfasst.
EP18723605.4A 2017-05-03 2018-04-26 Uhrvorrichtung mit positionierorgan Active EP3619579B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17169280.9A EP3399373A1 (de) 2017-05-03 2017-05-03 Uhrvorrichtung mit positionierorgan
PCT/IB2018/052896 WO2018203187A1 (fr) 2017-05-03 2018-04-26 Dispositif horloger a organe de positionnement.

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EP3619579A1 EP3619579A1 (de) 2020-03-11
EP3619579B1 true EP3619579B1 (de) 2021-06-09

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EP18723605.4A Active EP3619579B1 (de) 2017-05-03 2018-04-26 Uhrvorrichtung mit positionierorgan

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3907563B1 (de) * 2020-05-07 2022-09-14 Patek Philippe SA Genève Uhrwerkmechanismus, das ein schwenkorgan umfasst

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4134624C1 (en) * 1991-10-19 1993-07-08 Iwc International Watch Co. Ag, Schaffhausen, Ch Stop spring for actuating or fixing rotational position of gear of clock gear train - has spring arm with one end fixable at locally secured part and locking tooth at other free end moving inwards under preloading effect of arm to engage in gear tooth gap

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2645189B1 (de) * 2012-03-29 2016-02-03 Nivarox-FAR S.A. Flexibler Uhrhemmungsmechanismus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4134624C1 (en) * 1991-10-19 1993-07-08 Iwc International Watch Co. Ag, Schaffhausen, Ch Stop spring for actuating or fixing rotational position of gear of clock gear train - has spring arm with one end fixable at locally secured part and locking tooth at other free end moving inwards under preloading effect of arm to engage in gear tooth gap

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3907563B1 (de) * 2020-05-07 2022-09-14 Patek Philippe SA Genève Uhrwerkmechanismus, das ein schwenkorgan umfasst

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EP3399373A1 (de) 2018-11-07
WO2018203187A1 (fr) 2018-11-08
EP3619579A1 (de) 2020-03-11

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