EP3479175B1 - Mechanisches uhrwerk - Google Patents
Mechanisches uhrwerk Download PDFInfo
- Publication number
- EP3479175B1 EP3479175B1 EP17733911.6A EP17733911A EP3479175B1 EP 3479175 B1 EP3479175 B1 EP 3479175B1 EP 17733911 A EP17733911 A EP 17733911A EP 3479175 B1 EP3479175 B1 EP 3479175B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- striker
- oscillator
- preferably greater
- energy
- impulse
- 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.)
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- 230000005540 biological transmission Effects 0.000 claims description 10
- 239000000463 material Substances 0.000 claims description 9
- 238000004519 manufacturing process Methods 0.000 claims description 6
- 229910000831 Steel Inorganic materials 0.000 claims description 5
- 239000005300 metallic glass Substances 0.000 claims description 5
- 229910052710 silicon Inorganic materials 0.000 claims description 5
- 239000010703 silicon Substances 0.000 claims description 5
- 239000010959 steel Substances 0.000 claims description 5
- 230000005484 gravity Effects 0.000 claims description 4
- PNEYBMLMFCGWSK-UHFFFAOYSA-N Alumina Chemical compound [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 claims 12
- 238000000034 method Methods 0.000 claims 10
- 238000004804 winding Methods 0.000 description 23
- 230000035939 shock Effects 0.000 description 16
- 230000009471 action Effects 0.000 description 9
- 238000010304 firing Methods 0.000 description 8
- 238000006243 chemical reaction Methods 0.000 description 5
- 239000010979 ruby Substances 0.000 description 4
- 229910001750 ruby Inorganic materials 0.000 description 4
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- 238000013519 translation Methods 0.000 description 3
- 241000209149 Zea Species 0.000 description 2
- 235000005824 Zea mays ssp. parviglumis Nutrition 0.000 description 2
- 235000002017 Zea mays subsp mays Nutrition 0.000 description 2
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- 230000010355 oscillation Effects 0.000 description 2
- 230000000284 resting effect Effects 0.000 description 2
- VYPSYNLAJGMNEJ-UHFFFAOYSA-N Silicium dioxide Chemical compound O=[Si]=O VYPSYNLAJGMNEJ-UHFFFAOYSA-N 0.000 description 1
- 238000000563 Verneuil process Methods 0.000 description 1
- 230000000739 chaotic effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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- 210000000056 organ Anatomy 0.000 description 1
- TWNQGVIAIRXVLR-UHFFFAOYSA-N oxo(oxoalumanyloxy)alumane Chemical compound O=[Al]O[Al]=O TWNQGVIAIRXVLR-UHFFFAOYSA-N 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- SBEQWOXEGHQIMW-UHFFFAOYSA-N silicon Chemical compound [Si].[Si] SBEQWOXEGHQIMW-UHFFFAOYSA-N 0.000 description 1
- 229910052814 silicon oxide Inorganic materials 0.000 description 1
Images
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
- G04B1/00—Driving mechanisms
- G04B1/10—Driving mechanisms with mainspring
- G04B1/22—Compensation of changes in the motive power of the mainspring
- G04B1/225—Compensation of changes in the motive power of the mainspring with the aid of an interposed power-accumulator (secondary spring) which is always tensioned
-
- G—PHYSICS
- G04—HOROLOGY
- G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
- G04B15/00—Escapements
- G04B15/10—Escapements with constant impulses for the regulating mechanism
-
- G—PHYSICS
- G04—HOROLOGY
- G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
- G04B15/00—Escapements
- G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
Definitions
- the present invention relates to a mechanical clock movement.
- a traditional mechanical watch movement comprises a source of energy, such as a barrel, a going train driven by the energy source, an escapement driven by the going train and an oscillator whose oscillations are maintained by the 'exhaust.
- the oscillator (or regulating organ) is generally of the balance-spring type.
- the escapement generally comprises an escape wheel (coaxial and integral wheel and pinion) and an anchor. The pinion of the escapement wheel meshes with the last wheel of the going train while the wheel of the escapement wheel cooperates with the lever, which communicates mechanical energy pulses to the oscillator.
- Some movements also include, in the going train between the energy source and the escapement, a so-called “constant-force” device, that is to say a device comprising an intermediate spring periodically charged by the same amount by the source of energy and supplying its energy to the exhaust.
- a constant-force device makes it possible to make the oscillations of the oscillator independent of the winding state of the energy source.
- the efficiency of a mechanical clock movement is low. Indeed, the escapement transmits to the oscillator only a small part of the energy which it receives.
- One of the causes of the observed energy losses is friction between the different parts.
- the striker accompanies (remains in contact with) the oscillator over a pulse angle which is generally between 12° and 20°.
- a pulse angle which is generally between 12° and 20°.
- Such a chaotic transmission of energy between the striker and the oscillator is an additional obstacle to obtaining good efficiency.
- the present invention aims to provide a clock movement with improved performance.
- the striker transmits all its kinetic energy to the oscillator in a single shock and its speed becomes zero immediately after the shock, so that the accompanying phenomenon between the striker and the oscillator and the energy losses that it causes do not exist in the present invention.
- the present invention proposes a clock movement according to independent claim 2.
- the present invention also proposes a method of making a clock movement according to independent claim 9.
- the present invention proposes a method for producing a clock movement according to independent claim 10.
- a mechanical timepiece movement comprises an energy source 1, typically consisting of one or more barrels, a going train 2, an escapement 3 and an oscillator 4.
- the energy source 1 and the train finishing 2 are conventional, so they will not be described.
- Oscillator 4 is also of conventional type. It comprises, mounted on a balance shaft 6 of axis A, a balance-spring (not shown) and a double plateau.
- the double chainring includes a large chainring 7, which carries a chainring peg 8, and a small chainring 9.
- the escapement 3 is of the type described in the patent applications WO 99/64936 , WO 2009/118310 and CH 705674 . It thus comprises two escapement wheels (not shown), a bistable leaf spring 10, a winding rocker 11 and a striker or trigger rocker 12.
- the two escapement mobiles each comprise a pinion which meshes with the last wheel of the going train 2 and an escapement wheel provided not with teeth but with winding cams each terminated by a locking abutment.
- the two escape wheels cooperate respectively and alternately with escape pins 13 carried by the winding rocker 11.
- the winding rocker 11 and the striker 12 pivot around the same axis B which corresponds to the midpoint of the leaf spring 10.
- the axis B is for example the axis of a rod driven into the rocker winding 11, pivoting in the bearings of the movement frame and around which the striker 12 pivots.
- the leaf spring 10 is integral with the striker 12 and with an outer frame (not shown) which surrounds the leaf spring 10, and consists of two elastic blades 10a, 10b each having one end joined to the striker 12 and another end joined to the external frame, fixed to the frame of the movement.
- the leaf spring 10 has two convexities of opposite directions on either side of its midpoint and can pass from a first stable state to a second stable state by reversing the direction of each of the two convexities.
- the leaf spring 10 is either prestressed so as to work in buckling or preformed so as to, in the rest state, already present two convexities as described in the international patent application WO 2017/032528 of the present plaintiff.
- the outer frame is deformable to allow buckling of the leaf spring 10.
- the outer frame is rigid.
- the winding rocker 11 comprises two arms 14 carrying at their ends two pins 14a, 14b engaged in eyelets (not shown) of the two elastic blades 10a, 10b respectively.
- An inverse configuration is of course possible where the pins 14a, 14b would be carried by the elastic blades 10a, 10b, respectively, to engage in eyelets of the winding rocker 11.
- other modes of connection between the winding rocker 11 and the elastic blades 10a, 10b can be envisaged, for example two pins at the end of each arm 14 of the winding rocker 11 pinching the corresponding elastic blade.
- the firing pin 12 comprises a body 15 surrounding the axis B and extended on one side by a fork 16-17 and on the other side by a shank 18.
- the fork 16-17 performs the function of an anchor fork traditional, namely cooperating with the plate pin 8 to communicate mechanical energy pulses to the oscillator 4, and comprises for this purpose a first horn 16 and a second horn 17.
- a stinger 19 secured to the striker 12 is capable of cooperate with the small plate 9 of the oscillator 4 to prevent the overturning of the striker 12 in the event of an impact.
- the tail 18 is itself arranged to cooperate with first and second limit stops 20, 21 fixed relative to the frame of the movement, for example in one piece with the aforementioned outer frame, to limit the angular displacement of the striker 12.
- the winding rocker 11 actuated by a winding cam of one of the escape wheels and acting symmetrically in the zone of the two convexities of the leaf spring 10, deforms the leaf spring 10 from a first from its stable states to a metastable state close to an unstable state corresponding to fourth mode buckling, to wind the leaf spring 10.
- This winding phase ends when the winding rocker 11 is blocked by a Escape wheel locking abutment with which it cooperates, which maintains the leaf spring 10 in its metastable state and immobilizes the two escapement wheels, the going train 2 and the winding rocker 11.
- the striker 12 located in the zone of the midpoint of the leaf spring 10 acts on the leaf spring 10 to cause it to exceed its unstable state and thus cause it to switch into its second stable state by releasing its energy.
- the energy allowing striker 12 to deform leaf spring 10 beyond its unstable state from its metastable state is provided by oscillator 4, when chainring pin 8 strikes horn 16 of the fork.
- This phase which requires only a small input of energy, can be compared to the release phase of a lever escapement.
- the relaxation of the leaf spring 10, that is to say its passage from its unstable state to its second stable state abruptly changes the inclination of the midpoint zone, which causes the striker 12 to pivot, which then communicates an impulse to the plate pin 8 by its horn 17.
- the figures 2 to 10 represent the different operating phases of the escapement and the oscillator.
- the oscillator 4 is in the acceleration phase and traverses the descending sinister angle, the striker 12 is resting against the limiting abutment 20 and the leaf spring 10 is at the end of winding (metastable state).
- the oscillator 4 is close to its maximum speed and begins to traverse the left angle of lift, the horn 16 of the firing pin 12 is struck by the plate pin 8 (release, by a single shock) and the leaf spring 10 is unlocked (between the metastable state and the unstable state).
- the oscillator 4 is at its maximum speed and traverses the left angle of lift, the striker 12 strikes by its horn 17 the pin of the plate 8 to give it an impulse (by a single shock as will be explained later) then that the leaf spring 10 has just switched from the unstable state to the second stable state.
- oscillator 4 decelerates and traverses the ascending left angle, the striker 12 bears against the limit stop 21 and the leaf spring 10 is at the start of winding (it leaves the second stable state).
- the rotation of the oscillator 4 is reversed (maximum left elongation), the striker 12 is resting against the limiting abutment 21 and the leaf spring 10 is being wound (between the second stable state and the metastable state).
- the oscillator 4 is close to its maximum speed and begins to travel through the dexter lift angle, the horn 17 of the firing pin 12 is struck by the plate pin 8 (release, by a single shock) and the leaf spring 10 is unlocked (between the metastable state and the unstable state).
- the oscillator 4 is at its maximum speed and travels through the dexter lift angle, the striker 12 strikes by its horn 16 the plate pin 8 to give it an impulse (by a single shock as will be explained later) then that the leaf spring 10 has just switched from the unstable state to the first stable state.
- the oscillator 4 decelerates and traverses the dexter ascending angle, the striker 12 bears against the limiting abutment 20 and the leaf spring 10 is at the start of winding (it leaves the first stable state).
- escapement 3 finds itself in the phase illustrated in figure 2 and the sequence of figures 2 to 10 repeating itself.
- the angle of impulse ie the angle traveled by the striker between the start of the impulse and the end of the impulse, is between 12° and 20°.
- this pulse angle is very small, typically less than 1.5° or even 1°.
- the various parameters of the movement in particular the quantity of mechanical energy stored in the leaf spring 10 at each of its windings, the geometry of the striker 12 and the moments of inertia of the striker 12 and of the oscillator 4, are chosen in such a way that the striker 12 transfers all its kinetic energy to the oscillator 4 in a single shock ( figure 4 and 8 ), the firing pin 12 having zero speed just after the impact, the residual energy in the leaf spring 10 then bringing the striker 12 to rest against one of the limiting stops 20, 21 ( figure 5 and 9 ).
- the speed of the striker 12 will be zero just after the impact. , which implies that all of its kinetic energy will have been communicated to oscillator 4 and that striker 12 will not accompany oscillator 4. This results in a significant improvement in the efficiency of the escapement and in the chronometry of the movement.
- the spacing E of the horns 16, 17 is greater than 1.5 times, preferably 1.6 times, preferably 1.7 times, preferably 1.8 times, preferably 1.9 times, more preferably 2 times, the diameter D of the plate pin 8.
- diameter of the chainring peg we mean its diameter strictly speaking, in particular when the chainring peg is of semi-circular shape. as shown, or more generally its largest dimension perpendicular to the plane which contains the axis of rotation A of the oscillator 4 and which constitutes a plane of symmetry for the platter pin 8.
- the platter pin 8 may have other shapes than that shown, for example the shape of a finger or part of a finger extending radially from an annular part mounted on the balance shaft 6.
- the wide spacing E of the lugs 16, 17 promotes the exit of the pin 8 from the fork 16-17 after the impulse by allowing it, given the zero speed of the striker 12, to leave said fork without touching the other horn than that having communicated the impulse to it. Thanks to this feature too, the efficiency of the escapement and the chronometry of the movement are improved.
- the impulse communicated by the striker 12 to the oscillator 4 occurs while the plate pin 8 is on the center line, that is to say while the plate pin 8 is crossed symmetrically by the plane containing the axis of rotation A of the oscillator 4 and the axis of rotation B of the striker 12.
- This position of the plate pin 8 corresponds to the equilibrium position of the oscillator 4.
- Communicate the impulse on the line of centers makes it possible not to affect the isochronism of the oscillator.
- a pulse after the line of the centers gives a delay to the movement but, thanks to the unique shock that the pulse produces in the present invention, this delay will remain constant so that it can be corrected by a simple adjustment of the inertia. of the balance wheel and/or the active length of the hairspring.
- the striker 12 (or at least the fork 16-17) and the pin 8 are each made of one of the following materials: steel, preferably tempered; aluminum oxide, preferably ruby, more preferably ruby obtained by the Verneuil process; silicon, preferably monocrystalline, preferably also coated with silicon oxide; metallic glass. All combinations of these materials are possible to form the couple of materials of the striker 12 and the pin 8.
- the firing pin 12 illustrated in figures 2 to 11 is balanced, in other words its geometry is chosen so that its center of gravity is located on its axis of rotation B. Such a striker shape makes the latter insensitive to the linear shocks received by the clockwork movement.
- the figure 12 shows a variant of the firing pin used in the present invention. According to this variant, the striker, designated by 12 ', is not balanced but on the contrary has an unbalance which confers on it in particular two arms 22, 23 which extend the lugs 16, 17. These two arms 22, 23, located on the 'other side of the axis of rotation B relative to the tail 18, replace said tail. They thus cooperate respectively with limiting stops 20', 21' to limit the angular movement of the striker 12'.
- the unbalance of the striker 12' is chosen so that during the shocks (impulses) communicated by the striker 12' to the plate pin 8 the reaction forces at the level of the axis of rotation B are minimal, thus making it possible to optimize the transmission of energy between striker 12' and oscillator 4 and therefore the efficiency of the escapement.
- the present invention is not limited to a rotary striker.
- the striker can in fact be mobile in translation rather than in rotation, like the 12" striker illustrated in figure 13 .
- Such a movable striker in translation can be actuated for example by a movable frame of the type described in the patent application WO 2013/144236 .
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- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Micromachines (AREA)
- Springs (AREA)
Claims (16)
- Uhrwerk, das einen Oszillator (4), der um eine erste Achse (A) drehbar ist, ein Schlagstück (12), das um eine zweite Achse (B) drehbar ist, um mechanische Energieimpulse auf den Oszillator (4) zu übertragen, eine Energiequelle (1) und eine Übertragungsvorrichtung (1 bis 3) umfasst, welche die Energiequelle (1) mit dem Schlagstück (12) verbindet, wobei die Übertragungsvorrichtung (1 bis 3) eine Konstantkraftvorrichtung (10) zum periodischen Speichern einer an das Schlagstück (12) zu liefernden Energiemenge umfasst, wobei die Konstantkraftvorrichtung (10) ein bistabiles elastisches Organ umfasst, das Schlagstück (12) oder der Oszillator (4) eine Gabel (16, 17) umfasst, die dazu gestaltet ist, mit einem Stift (8) des Oszillators (4) beziehungsweise des Schlagstücks (12) zusammenzuwirken, die Gabel ein erstes und ein zweites Horn (16, 17) umfasst, die Gabel (16 und 17) und der Stift (8) jeweils aus einem der folgenden Materialien hergestellt sind: Stahl, Aluminiumoxid, Silizium, metallisches Glas, dadurch gekennzeichnet, dass die Energiemenge, die Geometrie des Schlagstücks (12) und die Trägheitsmomente des Schlagstücks (12) und des Oszillators (4) derart ausgewählt sind, dass bei jedem Impuls, der von dem Schlagstück (12) auf den Oszillator (4) übertragen wird, die folgende Beziehung im Wesentlichen erfüllt ist:
- Uhrwerk, das einen Oszillator (4), der um eine Achse (A) drehbar ist, ein Schlagstück (12") mit linearer Verlagerung, um mechanische Energieimpulse auf den Oszillator (4) zu übertragen, eine Energiequelle (1) und eine Übertragungsvorrichtung (1 bis 3) umfasst, welche die Energiequelle (1) mit dem Schlagstück (12") verbindet, wobei die Übertragungsvorrichtung (1 bis 3) eine Konstantkraftvorrichtung zum periodischen Speichern einer an das Schlagstück (12") zu liefernden Energiemenge umfasst, wobei die Konstantkraftvorrichtung (10) ein bistabiles elastisches Organ umfasst, das Schlagstück (12") oder der Oszillator (4) eine Gabel (16, 17) umfasst, die dazu gestaltet ist, mit einem Stift (8) des Oszillators (4) beziehungsweise des Schlagstücks (12") zusammenzuwirken, wobei die Gabel ein erstes und ein zweites Horn (16, 17) umfasst, wobei die Gabel (16 und 17) und der Stift (8) jeweils aus einem der folgenden Materialien hergestellt sind: Stahl, Aluminiumoxid, Silizium, metallisches Glas, dadurch gekennzeichnet, dass die Energiemenge, die Geometrie des Schlagstücks (12") und das Trägheitsmoment des Oszillators (4) derart ausgewählt sind, dass bei jedem Impuls, der von dem Schlagstück (12") auf den Oszillator (4) übertragen wird, die folgende Beziehung im Wesentlichen erfüllt ist:
- Uhrwerk nach Anspruch 1, dadurch gekennzeichnet, dass das Verhältnis I2/I1 größer als 10, vorzugsweise größer als 50, vorzugsweise größer als 100, vorzugsweise größer als 500, vorzugsweise noch größer als 1000, ist.
- Uhrwerk nach Anspruch 2, dadurch gekennzeichnet, dass das Verhältnis I2/(m1·d2 2) größer als 10, vorzugsweise größer als 50, vorzugsweise größer als 100, vorzugsweise größer als 500, vorzugsweise noch größer als 1000, ist.
- Uhrwerk nach Anspruch 1 oder 3, dadurch gekennzeichnet, dass das Schlagstück (12') ein Ungleichgewicht aufweist, das so ausgewählt ist, dass die folgende Beziehung im Wesentlichen erfüllt ist:
- Uhrwerk nach Anspruch 1, 3 oder 5, dadurch gekennzeichnet, dass die Energiemenge, die Geometrie des Schlagstücks (12) und die Trägheitsmomente des Schlagstücks (12) und des Oszillators (4) derart ausgewählt sind, dass der Impulswinkel, den das Schlagstück (12) bei jedem auf den Oszillator (4) übertragenen Impuls zurücklegt, kleiner als 1,5°, vorzugsweise kleiner als 1°, ist.
- Uhrwerk nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Schlagstück (12) und der Oszillator (4) so gestaltet sind, dass jeder der Impulse auf den Oszillator (4) übertragen wird, während er sich im Wesentlichen in seiner Gleichgewichtswinkelposition befindet.
- Uhrwerk nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Schlagstück (12) und der Oszillator (4) so gestaltet sind, dass jeder der Impulse auf den Oszillator (4) übertragen wird, während er sich nach seiner Gleichgewichtswinkelposition befindet.
- Verfahren zur Herstellung eines Uhrwerks, das einen Oszillator (4), der um eine erste Achse (A) drehbar ist, ein Schlagstück (12), das um eine zweite Achse (B) drehbar ist, um mechanische Energieimpulse auf den Oszillator (4) zu übertragen, eine Energiequelle (1) und eine Übertragungsvorrichtung (1 bis 3) umfasst, welche die Energiequelle (1) mit dem Schlagstück (12) verbindet, wobei die Übertragungsvorrichtung (1 bis 3) eine Konstantkraftvorrichtung (10) zum periodischen Speichern einer an das Schlagstück (12) zu liefernden Energiemenge umfasst, wobei die Konstantkraftvorrichtung (10) ein bistabiles elastisches Organ umfasst, das Schlagstück (12) oder der Oszillator (4) eine Gabel (16, 17) umfasst, die dazu gestaltet ist, mit einem Stift (8) des Oszillators (4) beziehungsweise des Schlagstücks (12) zusammenzuwirken, die Gabel ein erstes und ein zweites Horn (16, 17) umfasst, die Gabel (16 und 17) und der Stift (8) jeweils aus einem der folgenden Materialien hergestellt sind: Stahl, Aluminiumoxid, Silizium, metallisches Glas, wobei das Verfahren einen Schritt der Gestaltung des Uhrwerks, gefolgt von einem Schritt der Herstellung des Uhrwerks umfasst, wobei das Verfahren dadurch gekennzeichnet ist, dass bei der Gestaltung des Uhrwerks die Energiemenge, die Geometrie des Schlagstücks (12) und die Trägheitsmomente des Schlagstücks (12) und des Oszillators (4) derart ausgewählt werden, dass bei jedem Impuls, der von dem Schlagstück (12) auf den Oszillator (4) übertragen wird, die folgende Beziehung im Wesentlichen erfüllt wird:
- Verfahren zur Herstellung eines Uhrwerks, das einen Oszillator (4), der um eine Achse (A) drehbar ist, ein Schlagstück (12") mit linearer Verlagerung, um mechanische Energieimpulse (4) auf den Oszillator (4) zu übertragen, eine Energiequelle (1) und eine Übertragungsvorrichtung (1 bis 3) umfasst, welche die Energiequelle (1) mit dem Schlagstück (12") verbindet, wobei die Übertragungsvorrichtung (1 bis 3) eine Konstantkraftvorrichtung zum periodischen Speichern einer an das Schlagstück (12") zu liefernden Energiemenge umfasst, wobei die Konstantkraftvorrichtung (10) ein bistabiles elastisches Organ umfasst, das Schlagstück (12") oder der Oszillator (4) eine Gabel (16, 17) umfasst, die dazu gestaltet ist, mit einem Stift (8) des Oszillators (4) beziehungsweise des Schlagstücks (12") zusammenzuwirken, wobei die Gabel ein erstes und ein zweites Horn (16, 17) umfasst, die Gabel (16 und 17) und der Stift (8) jeweils aus einem der folgenden Materialien hergestellt sind: Stahl, Aluminiumoxid, Silizium, metallisches Glas, wobei das Verfahren einen Schritt der Gestaltung des Uhrwerks, gefolgt von einem Schritt der Herstellung des Uhrwerks umfasst, wobei das Verfahren dadurch gekennzeichnet ist, dass bei der Gestaltung des Uhrwerks die Energiemenge, die Geometrie und die Masse des Schlagstücks (12") und das Trägheitsmoment des Oszillators (4) derart ausgewählt werden, dass bei jedem Impuls, der von dem Schlagstück (12") auf den Oszillator (4) übertragen wird, die folgende Beziehung im Wesentlichen erfüllt wird:
- Verfahren nach Anspruch 9, dadurch gekennzeichnet, dass das Verhältnis I2/I1 größer als 10, vorzugsweise größer als 50, vorzugsweise größer als 100, vorzugsweise größer als 500, vorzugsweise noch größer als 1000, ist.
- Verfahren nach Anspruch 10, dadurch gekennzeichnet, dass das Verhältnis I2/(m1·d2 2) größer als 10, vorzugsweise größer als 50, vorzugsweise größer als 100, vorzugsweise größer als 500, vorzugsweise noch größer als 1000, ist.
- Verfahren nach Anspruch 9 oder 11, dadurch gekennzeichnet, dass bei der Gestaltung des Uhrwerks für das Schlagstück (12') ein Ungleichgewicht derart ausgewählt wird, dass die folgende Beziehung im Wesentlichen erfüllt wird:
- Verfahren nach Anspruch 9, 11 oder 13, dadurch gekennzeichnet, dass bei der Gestaltung des Uhrwerks die Energiemenge, die Geometrie des Schlagstücks (12) und die Trägheitsmomente des Schlagstücks (12) und des Oszillators (4) derart ausgewählt werden, dass der Impulswinkel, den das Schlagstück (12) bei jedem auf den Oszillator (4) übertragenen Impuls zurücklegt, kleiner als 1,5°, vorzugsweise kleiner als 1°, ist.
- Verfahren nach einem der Ansprüche 9 bis 14, dadurch gekennzeichnet, dass das Schlagstück (12) und der Oszillator (4) so gestaltet sind, dass jeder der Impulse auf den Oszillator (4) übertragen wird, während er sich im Wesentlichen in seiner Gleichgewichtswinkelposition befindet.
- Verfahren nach einem der Ansprüche 9 bis 14, dadurch gekennzeichnet, dass das Schlagstück (12) und der Oszillator (4) so gestaltet sind, dass jeder der Impulse auf den Oszillator (4) übertragen wird, während er sich nach seiner Gleichgewichtswinkelposition befindet.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP16176831 | 2016-06-29 | ||
PCT/IB2017/053706 WO2018002778A1 (fr) | 2016-06-29 | 2017-06-21 | Mouvement d'horlogerie mecanique |
Publications (2)
Publication Number | Publication Date |
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EP3479175A1 EP3479175A1 (de) | 2019-05-08 |
EP3479175B1 true EP3479175B1 (de) | 2022-11-09 |
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Application Number | Title | Priority Date | Filing Date |
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EP17733911.6A Active EP3479175B1 (de) | 2016-06-29 | 2017-06-21 | Mechanisches uhrwerk |
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EP (1) | EP3479175B1 (de) |
WO (1) | WO2018002778A1 (de) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2487546A1 (de) * | 2011-02-11 | 2012-08-15 | Montres Journe S.A. | Zweiachsiges Hochleistungsauspuffsystem, d.h. EBHP |
EP2863272A1 (de) * | 2013-10-16 | 2015-04-22 | Montres Breguet SA | Hemmungsmechanismus für Uhrwerk einer Armbanduhr |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999064936A1 (fr) | 1998-06-08 | 1999-12-16 | Manufacture Des Montres Rolex S.A. | Procede pour transmettre des impulsions d'energie mecanique d'unesource motrice a un regulateur oscillant |
CH708113B1 (de) * | 2007-09-13 | 2014-12-15 | Stéphane Von Gunten | Anker für eine Uhrenhemmung. |
EP2105806B1 (de) | 2008-03-27 | 2013-11-13 | Sowind S.A. | Hemmungsmechanismus |
CH703464B1 (fr) * | 2010-07-19 | 2013-11-29 | Nivarox Sa | Mécanisme oscillant à pivot élastique. |
CH705674B1 (fr) | 2011-10-27 | 2016-11-30 | Sowind S A | Mécanisme d'échappement. |
JP5918438B2 (ja) | 2012-03-29 | 2016-05-18 | ニヴァロックス−ファー ソシエテ アノニム | 可動フレームを備えた可撓性エスケープ機構 |
EP3338144B1 (de) | 2015-08-21 | 2019-09-25 | Patek Philippe SA Genève | Bistabile mechanische vorrichtung für uhrwerke |
-
2017
- 2017-06-21 EP EP17733911.6A patent/EP3479175B1/de active Active
- 2017-06-21 WO PCT/IB2017/053706 patent/WO2018002778A1/fr unknown
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2487546A1 (de) * | 2011-02-11 | 2012-08-15 | Montres Journe S.A. | Zweiachsiges Hochleistungsauspuffsystem, d.h. EBHP |
EP2863272A1 (de) * | 2013-10-16 | 2015-04-22 | Montres Breguet SA | Hemmungsmechanismus für Uhrwerk einer Armbanduhr |
Also Published As
Publication number | Publication date |
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WO2018002778A1 (fr) | 2018-01-04 |
EP3479175A1 (de) | 2019-05-08 |
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