EP3399373A1 - Uhrvorrichtung mit positionierorgan - Google Patents

Uhrvorrichtung mit positionierorgan Download PDF

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Publication number
EP3399373A1
EP3399373A1 EP17169280.9A EP17169280A EP3399373A1 EP 3399373 A1 EP3399373 A1 EP 3399373A1 EP 17169280 A EP17169280 A EP 17169280A EP 3399373 A1 EP3399373 A1 EP 3399373A1
Authority
EP
European Patent Office
Prior art keywords
positioning member
elastic
support
engagement
wheel
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.)
Withdrawn
Application number
EP17169280.9A
Other languages
English (en)
French (fr)
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Patek Philippe SA Geneve filed Critical Patek Philippe SA Geneve
Priority to EP17169280.9A priority Critical patent/EP3399373A1/de
Priority to EP18723605.4A priority patent/EP3619579B1/de
Priority to PCT/IB2018/052896 priority patent/WO2018203187A1/fr
Publication of EP3399373A1 publication Critical patent/EP3399373A1/de
Withdrawn legal-status Critical Current

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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 clock device including a positioning member such as a jumper or a pawl.
  • a jumper is a lever terminated by two inclined planes which support between the tips of two consecutive teeth of a wheel, also called star, under the action of a spring, to maintain it in a certain angular position.
  • the teeth lift the jumper which then falls between two other teeth.
  • a jumper allows the movement of the wheel in both directions.
  • a ratchet is a lever provided with a spout which enters the toothing of a wheel under the action of a spring to maintain it in a certain angular position.
  • the teeth When the wheel in question is actuated in a specific direction, the teeth lift the ratchet which then falls between two other teeth. In the other direction, the pawl prevents the wheel from turning by the shape of its nose and / or the teeth of the wheel.
  • jumpers and ratchets are built on the basis of leaf springs working in flexion.
  • the moment of force exerted on the wheel is necessary to keep it in position.
  • the moment of force required for the rotation of a pitch of the wheel must overcome the resistance exerted by the jumper or the pawl, which leads to a certain consumption of energy.
  • the moment of force required to initiate the rotation of the wheel should not be too low.
  • the maximum resistance exerted by the jumper or the ratchet when rotating a step of the wheel does not exceed a certain value so that the wheel is able to overcome it, otherwise the mechanism watchmaker could hang.
  • the jumpers and ratchets currently used generate a peak energy consumption corresponding to maximum resistance.
  • the aim of the invention is to propose a watchmaking device comprising a toothed component and a positioning member, said positioning member ensuring a good positional retention of the toothed component while at the same time reducing or even eliminating any peak in power consumption during operation. advancement of a pitch of said toothed component.
  • the invention provides a device according to claim 1.
  • the invention also provides a timepiece such as a wristwatch or a pocket watch comprising such a clock device.
  • a watch device 1 intended to be part of a watch mechanism such as a movement or an additional mechanism to the movement, comprises a wheel 11 having a toothing 111, and a positioning 10.
  • the toothing 111 is typically a toothing with truncated teeth.
  • the positioning member 10 shown in FIG. figure 1 is a ratchet. It keeps the wheel 11 in position and allows its rotation only in the counterclockwise direction, as indicated by the arrow B.
  • 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 a plurality of distributed resilient blades, preferably uniformly , around the support 12. These resilient blades 14 connect the support 12 to the engagement member 15 which is itself engaged in the toothing 111 of the wheel 11 to be positioned.
  • the positioning member 10 shown in figures 1 and 2 further comprises a serge 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 on a fixed or movable frame 100, on which is also mounted the wheel 11, said frame 100 typically comprising the plate bearing the watch mechanism.
  • the serge 13 and the engagement element 15 integral with it are guided in rotation relative 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 moment of return tending to pivot the serge 13 around the support 12 in the counterclockwise direction of the figures 1 and 2 .
  • the rotation of the serge 13 in the counterclockwise direction is limited by a stop 16, fixed on the frame 100, against which a protrusion 17 of the serge 13 is supported, when the device 1 is in the rest position, that is, when the engagement member 15 is centrally engaged in a recess 11a of the toothing 111 between two consecutive teeth of the wheel 11, as illustrated in FIG. figure 1 .
  • the figure 2 represents, for the understanding of the invention, the isolated positioning member 10, that is to say free of any interaction with the abutment 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 serge 13, and therefore of its engagement element 15, with respect to its support 12, this sense being defined as that which allows, from a state of rest of said isolated positioning member 10 in which all its elastic blades 14 are at rest, the largest displacement relative angle of the engagement member 15 relative to the support 12.
  • the arrow A shown on the figures 1 and 2 illustrates this preferred direction of rotation of the engagement member 15 relative to the support 12; this meaning corresponds to the clockwise direction in these figures.
  • ⁇ be the angular position of the engagement element 15 of the positioning member 10 isolated with respect to the support 12, ⁇ being equal to zero when the isolated positioning member 10 is at rest, that is to say say when all its elastic blades 14 are at rest, and increasing with the relative angular displacement of the engagement member 15 relative 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 set of elastic strips 14 in the insulated positioning member 10 as a function of the angular position ⁇ of the engagement element 15 with respect to the support 12 .
  • the isolated positioning member 10 having a curve M ( ⁇ ) of the type of that shown in FIG. figure 3 differs from conventional elastic structures. Its properties are based on a sinuous shape of its elastic blades 14 which deform so as to generate a substantially constant elastic return moment (the curve M ( ⁇ ) has a plateau between ⁇ 1 and ⁇ 2 ) over a predetermined range of angular positions its engagement member 15 relative to its support 12. Obtaining such elastic blades requires a specific design and parameterized.
  • the topological optimization referred to in the above article uses parametric polynomial curves such as Bezier curves to determine the geometric shape of the elastic strips 14.
  • each of the elastic blades 14 of the positioning member 10 is a Bezier 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 inequation "(M max -M min ) / ((M max + M min ) / 2) ⁇ 0.05" corresponds to a constancy of the elastic return moment of 5% over an angular range.
  • the set of elastic blades 14 of the positioning member 10 of the device 1 is designed, in particular by its shape, to exert, in this member 10, a substantially constant elastic return moment (constancy of 5%) over a range of angular positions of the seam 13 and the engagement member 15 with respect to the support 12 by at least 10 °, preferably at least 15 °, more preferably at least 20 °.
  • this positioning member 10 is as follows: Outside diameter of the serge: 12 mm Outside diameter of the support: 2 mm Inside diameter of the serge: 10 mm Height: 0.12 mm Thickness of the 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 has been decomposed into two segments, a first segment corresponding to a curve of Bezier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bezier curve of order 4 based on control points Q 3 to Q 6 .
  • the graph of the figure 4 shows the geometry of the outer diameter of the support 12, the inner diameter of the serge 13 and 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 the set of point coordinates defined in Table 2 above.
  • This graph is made in an orthonormal frame.
  • FIGS. 5a and 5b represent the results of a simulation of the evolution of the elastic return moment of the particular positioning member 10 and realized as a function of the angular position ⁇ of its engagement element 15 with respect 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 where the elastic return moment reaches a local maximum. In the present invention, it is placed in this range [ ⁇ a , ⁇ b ] or at least partly in this range.
  • the positioning member 10 is 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 in a predetermined range of positions relative 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 a part of the range of positions [ ⁇ a , ⁇ b ] in which the stiffness of the set of 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 pivot the serge 13 and the engagement element 15 which it carries around the support 12 in the direction of the decrease of the angle ⁇ (counter-clockwise on the figure 1 ).
  • the engagement element 15 is positioned between two successive teeth of the toothing 111 of the wheel 11 to be positioned now. thus the latter in position under the effect of the moment of return 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 a pitch 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 element engagement 15 as well as the shape and dimensions of the toothing 111 of the toothed wheel 11 define, in turn, the upper limit of this range of positions.
  • the figure 6 presents the results of measurements of the moment of force noted 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 the arrow B .
  • the same toothed wheel 11, 71 has been 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 traditional positive stiffness (curve co) as shown in FIG. figure 7 .
  • the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises a commitment element 75 engaged in the toothing 711 of a toothed wheel 71.
  • This jumper 70 allows the rotation of the toothed wheel 71 in both directions (clockwise and counterclockwise respectively corresponding to the arrows G and F of the figure 7 ), however only the rotation in the counterclockwise direction (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 the arrow B ( figure 1 ) or arrow F ( figure 7 ).
  • the moment necessary to initiate the rotation of the wheel 11 or "start 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 about 0.084 N.mm.
  • the wheel 11 is therefore also held in position by the pawl consisting of the positioning member 10 according to the first embodiment of the invention than by the traditional jumper 70.
  • a noticeable difference is that the use of the traditional jumper (device 7, curve co) generates an operating peak of 0.135 N.mm which increases the energy consumption and may block the mechanism if the wheel 11 is not in operation. able to provide a moment of force sufficient to overcome this peak.
  • the time required to make turn the wheel 11 one step in the case of the device 1 has, meanwhile, no peak operation. On the contrary, it decreases constantly until reaching a value of 0.037 N.mm approximately corresponding to the time required to turn the wheel 11 when the engagement element 15 is opposite the truncated portion 11b of the toothing 111.
  • the watch 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 a pitch of the wheel to be positioned. compared to a traditional jumper 70 using a spring 74 with positive stiffness for holding in the equivalent position.
  • Such a watch device 1 also has the advantage of being less sensitive to linear shocks than jumpers or ratchets according to the prior art. This is due to the good balancing of its positioning member 10. This decrease in sensitivity to linear shocks can reduce the value of the start moment while maintaining good support in case of linear shocks and thus reduce overall consumption of energy during a rotation of a pitch 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 may for example be manufactured by machining, especially in the case where it is made of metal or an alloy such as Nivaflex ® , by DRIE etching in the case of silicon for example, or by molding, cutting, machining, especially in the case where it is made of plastic or metal glass.
  • the positioning member 10 may comprise only one elastic blade 14.
  • the serge 13 may also be interrupted and take the form of a circular arc, as shown in FIG. figure 8 .
  • the very structure of the positioning member 10 involves centering the support 12 with respect to its serge 13. However, it may comprise a device centering means for reinforcing the centering of the support 12.
  • a device typically comprises a rigid junction element 18, on the one hand, secured integrally to at least one zone of the serge 13 and secondly, positioned freely in rotation around of an axis 19, said axis 19 being integral with the support 12 and centered on the 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 FIG. figure 8 also includes such a centering device.
  • the watch device 1 may comprise a positioning member of a shape different from that illustrated in FIGS. figures 1 and 2 it may typically comprise elastic blades of a shape different from that illustrated in FIG. figure 4 . In particular, it may take a form as represented in figure 9 .
  • the positioning member 20 shown in FIG. figure 9 comprises a support 22 and a serge 23 connected by elastic blades 24, the serge 23 carrying an engagement element 25 intended to be engaged in the toothing of a toothed component to be positioned and held in this toothing under the effect of the moment restoring force exerted by all the elastic blades 24.
  • a watch device 3 according to a second embodiment of the invention comprises a wheel 31 having a toothing 311, and a positioning member 30.
  • the positioning member 30 is here a jumper. It keeps the wheel 31 in position and allows its rotation in both directions, both clockwise and counterclockwise, as indicated respectively by the arrows C and D at the figure 11 .
  • the positioning member 30 comprises a rigid element 33 movable and an elastic member 34 connecting the latter to a support 32 rigid.
  • 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 on a frame 300 on which is also mounted the wheel 31 and the rigid element 33 is movable relative to the support 32.
  • the frame 300 can be fixed or movable and typically comprises the plate carrying the mechanism or movement watchmaker including the device 3.
  • the rigid element 33 is guided in translation by the elastic blades 34 and moves along a straight line (d) passing preferably 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 member 35 moves with the remainder of the rigid member 33 along the straight 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 represented by the arrow E at the figure 11 .
  • the elastic blades 34 are here preformed flambé, that is to say they are machined with a flamed shape. They could however be preformed straight and work 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 movable parts relative to each other allowing adjustment of the compression. Each of them could also be preformed in the form of two half-straight V-shaped, and flaming only under the effect of its pre-arming.
  • the displacement 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 here considered without the abutment 36 and outside the device 3, that is to say free of any interaction with the toothed wheel 31.
  • This force was measured, for each position ⁇ , by measuring the opposite force required to hold the engagement member 35 in a given position.
  • the isolated positioning member 30 exhibiting an evolution of the force F ( ⁇ ) of the type of that represented in FIG. figure 13 differs from conventional elastic structures. Its properties are based on the ability of its elastic blades 34 to work in buckling, which allows it to behave as a bistable.
  • the Applicant has devised a particular positioning member comprising a pair of parallel resilient blades 34.
  • the dimensions of this positioning member 30 are those indicated in Table 1 below: ⁇ b> Table 1: ⁇ / b> Dimensions Unit Value
  • 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 member 35 along the line (d).
  • This model considers a monolithic 30 positioning member made of a cobalt based alloy, nickel and chromium, specifically Nivaflex ® 45/18 but any suitable material may be used.
  • materials such as silicon typically coated with silicon oxide, metallic glasses, mineral glasses, ceramic glasses, plastics or CK101 (non-alloy structural steel) are also suitable.
  • CK101 non-alloy structural steel
  • 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. In the present invention it is placed in this range or at least partly in this range.
  • the positioning member 30 is thus 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 in 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 tooth 311 of the wheel 31 to position, now the latter in position under the effect of the restoring force exerted by the pair of resilient blades 34, the positioning member 30 being armed with a value ⁇ arm in this position.
  • the choice of the value ⁇ arm defines the lower limit of the predetermined range of positions in which the engagement element 35 moves during the rotation of a pitch of the wheel 31.
  • the shape and dimensions of the teeth of the tooth 311 and the angle between the inclined planes defining the engagement element 35 are chosen so that the maximum value ⁇ reached during the rotation of a pitch of the wheel 31 is less than or equal to ⁇ 2 .
  • the stop 36 prevents the displacement of the engagement element 35 in the range of positions in which ⁇ is greater than ⁇ 2 . This is a security 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 shock or manipulation affecting the device 3.
  • the figure 14 presents the results of measurements of the moment of force noted 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 pitch in the direction of the arrow D of the figure 11 .
  • the same wheel 31, 71 has been 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 (curve co) as represented in figure 7 .
  • the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises a commitment element 75 engaged in the toothing 711 of a wheel 71.
  • This jumper 70 allows the rotation of the wheel 71 in both directions (clockwise and counterclockwise), however only the rotation in the counterclockwise direction (arrow F) has been studied here .
  • the angle ⁇ increases with the rotation of the wheel 31 (curve c 2 ) or 71 (curve c 0 ) respectively in the direction of the arrow D ( figure 11 ) or arrow F ( figure 7 ).
  • the moment necessary to initiate the rotation of the wheel 31 or "start moment” is approximately identical 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 conventional positive stiffness (0.084 N.mm).
  • the wheel 31 is thus 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 time required to turn the wheel 31 of a not in the case of the positioning member 30 (curve c 2 ) has, meanwhile, no peak operation. On the contrary, it decreases constantly until reaching a value almost zero, corresponding to the time required to rotate the wheel 31 when the engagement member 35 is opposite the truncated portion 31 b of the toothing 311.
  • the figure 14 shows therefore that both the jumper according to the second embodiment of the invention shown in FIG. figure 11 that the jumper 70 according to the prior art allow the repositioning of the toothed wheel 31, 71 to position.
  • the watch device 3 comprising a wheel 31 and a positioning member 30 according to the second embodiment of the invention makes it possible to reduce the maximum instantaneous energy consumption required during the rotation of a pitch of the wheel to be positioned by compared to a traditional jumper 70 using a spring 74 to positive stiffness for holding in the equivalent position.
  • the energy consumption is lower in the case of the use of the positioning member 30 than in the case of the use of a jumper 70 according to the prior art.
  • the watch device 3 studied thus makes it possible to reduce the overall energy consumption during a rotation of a 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 ratchets according to the prior art. This is due to the low weight of the moving parts of its positioning member 30 that are the elastic blades 34 and the engagement element 35. This low sensitivity to linear shocks can reduce the value of the start moment while retaining good support in case of linear shocks and so of further decrease the overall energy consumption during a rotation of a pitch of the gear wheel 31.
  • the low height of the blades 34 also reduces 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 is a jumper, the rotation of the wheel 31 is allowed in both directions, namely, in the direction of the arrow D but also in the direction of the arrow C ( figure 11 ) and the curve representing the moment of force noted on the wheel 31 to be positioned according to its angular displacement in the direction opposite to that studied would be identical to the curve c 2 .
  • the watch device 3 may comprise a positioning member of a shape different from that illustrated in FIGS. figures 11 and 12 .
  • it may take a form as represented 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 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 FIGS. figures 15 and 17 during the rotation of a step of this wheel 31, as for the figure 14 .
  • Each of these figures also represents the curve c 0 of the figure 14 for comparison.
  • the positioning member 40 shown in FIG. figure 15 differs from the positioning member 30 shown in FIG. figure 12 in that its element commitment 45 is truncated. This reduces the recoil of the engagement member 45 during the rotation of a pitch of the wheel 31 to be positioned.
  • the elements 42, 43, 44 of the variant represented in FIG. figure 15 corresponding to elements 32, 33, 34 of the variant represented in figure 12 .
  • the positioning member 50 shown in FIG. figure 17 differs from the positioning member 30 shown in FIG. figure 12 in that it furthermore has blades 59 working in flexion. This improves 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 FIG. figure 17 corresponding to the elements 32, 33, 34, 35 of the variant represented in figure 12 .
  • the positioning member 90 shown in FIG. figure 21 differs from the positioning member 30 shown in FIG. 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 FIG. figure 21 corresponding to elements 32, 33, 35 of the variant represented in figure 12 .
  • the rigid element 93 can optionally be guided along the straight line (d) previously defined by means of a guiding system including for example a finger and a groove. In the absence of such a guiding system, the elastic blade 94 of the positioning member 90 does not behave like a bistable but nevertheless has a negative stiffness over a predetermined range of positions of the engagement member 95. .
  • the positioning member 110 shown in FIG. figure 22 differs from the positioning member 90 shown in FIG. figure 21 in that its rigid element 113 and thus its engagement element 115 interrupt the elastic blade 114 outside its central part, in this case approximately 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 member 115 relative to the support 112.
  • the positioning member 120 shown in FIG. figure 23 is a variant of the intermediate positioning member between that represented in FIG. 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 respectively correspond to elements 32, 33, 35 of the variant represented in FIG. figure 12 .
  • the positioning member 130 shown in FIG. figure 24 differs from the positioning member 90 shown in FIG. figure 21 in that its elastic blade 134 comprises on either side of its rigid element 133, more precisely at each of the junctions of its elastic blade 134 with the support 132, a hinge 136, which is 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 retains a negative stiffness over a predetermined range of positions of the engagement member 135 relative to the 132.
  • the elements 132, 133, 135 of the variant shown in FIG. figure 22 corresponding to elements 92, 93, 95 of the variant shown in figure 21 .
  • such a positioning member 130 may comprise only one articulation 136, at a single junction of its elastic blade 134 with its support 132.
  • the positioning member 140 illustrated in FIG. figure 25 differs from the positioning member 90 shown in FIG. figure 21 in that it is not monolithic but obtained by assembling two parts, each of these parts defining a portion 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 FIG. figure 19a differs from the positioning member 90 shown in FIG. 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 straight line (d) and a second plane forming an angle of 85 ° with the straight line (d). ), as shown in figure 19b .
  • the slope difference of the inclined planes makes it possible to have a low starting moment with the slope of 85 ° and therefore a low energy consumption to initiate the rotation of the wheel 31. Moreover, this makes it possible to limit the effort Tangential on the jumper.
  • 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 FIG. figure 20 differs from the positioning member 30 shown in FIG. figure 12 in that it comprises a pair of elastic half-blades 84 to replace the pair of elastic blades 34.
  • the elements 82 and 83 of the variant represented in FIG. figure 20 correspond respectively to elements 32 and 33 of the variant shown in figure 12 .
  • the rigid element 83 comprises a protrusion 87 bearing against an abutment 86.
  • the fact that these elements bear against each other makes it possible to guide the engagement element 85 along the straight line (FIG. preferably passing through the center of the wheel 31. It is also possible to envisage an elastic system for translational guidance which makes it possible to avoid friction between the protuberance 87 of the rigid element 83 and the abutment 36.
  • the different variants of the positioning member that can be used in the device 3 according to the second mode embodiment of the invention can effectively position the wheel 31 to position with a decrease in overall energy consumption during the rotation of a pitch of said wheel 31.
  • These different variants have moreover the same advantages as those associated to the variant presented in the figure 11 . They allow in particular to eliminate the peak energy consumption occurring during the rotation of a pitch of the wheel 31 to be positioned with a conventional jumper using a spring with positive stiffness for holding in the equivalent position.
  • a watch device comprising an elastic member of a structure different from those presented.
  • any elastic member having a negative or zero stiffness over at least one position range may be suitable.
  • Those skilled in the art may further replace the toothed wheel to position one or the other of the two embodiments described by any other toothed component such as a rack for example.
  • the angle between the two inclined planes defined by the engagement member of the positioning member is typically between 120 ° and 170 ° but may be different.
  • the watch device has the advantage of eliminating the peak of energy consumption observed in the jumpers and ratchets conventionally used. It also makes it possible to reduce or even cancel the friction within the positioning member, especially 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 clock mechanism using ratchets or jumpers, which results in an increase in its reliability.
  • the device according to the invention is insensitive to linear shocks and advantageously allows a reduction in the overall energy consumption during the rotation of a pitch of its wheel.
  • the invention also relates to a timepiece such as a wristwatch or a pocket watch comprising such a watch device.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
EP17169280.9A 2017-05-03 2017-05-03 Uhrvorrichtung mit positionierorgan Withdrawn EP3399373A1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP17169280.9A EP3399373A1 (de) 2017-05-03 2017-05-03 Uhrvorrichtung mit positionierorgan
EP18723605.4A EP3619579B1 (de) 2017-05-03 2018-04-26 Uhrvorrichtung mit positionierorgan
PCT/IB2018/052896 WO2018203187A1 (fr) 2017-05-03 2018-04-26 Dispositif horloger a organe de positionnement.

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Application Number Priority Date Filing Date Title
EP17169280.9A EP3399373A1 (de) 2017-05-03 2017-05-03 Uhrvorrichtung mit positionierorgan

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

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EP3907563B1 (de) * 2020-05-07 2022-09-14 Patek Philippe SA Genève Uhrwerkmechanismus, das ein schwenkorgan umfasst

Citations (1)

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Publication number Priority date Publication date Assignee Title
EP2645189A1 (de) * 2012-03-29 2013-10-02 Nivarox-FAR S.A. Flexibler Uhrhemmungsmechanismus

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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

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EP2645189A1 (de) * 2012-03-29 2013-10-02 Nivarox-FAR S.A. Flexibler Uhrhemmungsmechanismus

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CHIA-WEN HOU: "Functional joint mechanisms with constant torque outputs", MECHANISM AND MACHINE THEORY, vol. 62, 2013, pages 166 - 181
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WO2018203187A1 (fr) 2018-11-08
EP3619579A1 (de) 2020-03-11

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