EP3599517B1 - Retrogrades tourbillon oder karussell eines uhrwerks - Google Patents

Retrogrades tourbillon oder karussell eines uhrwerks Download PDF

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Publication number
EP3599517B1
EP3599517B1 EP19187588.9A EP19187588A EP3599517B1 EP 3599517 B1 EP3599517 B1 EP 3599517B1 EP 19187588 A EP19187588 A EP 19187588A EP 3599517 B1 EP3599517 B1 EP 3599517B1
Authority
EP
European Patent Office
Prior art keywords
mobile
arm
wheel
energy source
retrograde
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
EP19187588.9A
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English (en)
French (fr)
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EP3599517A1 (de
Inventor
Johnny BÜHLER
Emmanuel BOUCHET
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.)
Harry Winston SA
Original Assignee
Harry Winston SA
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
Priority claimed from EP18185166.8A external-priority patent/EP3599515B1/de
Priority claimed from EP18185167.6A external-priority patent/EP3599516B1/de
Application filed by Harry Winston SA filed Critical Harry Winston SA
Publication of EP3599517A1 publication Critical patent/EP3599517A1/de
Priority to US16/912,183 priority Critical patent/US11493884B2/en
Priority to JP2020121197A priority patent/JP7063949B2/ja
Priority to RU2020123925A priority patent/RU2742378C1/ru
Priority to CN202010710207.3A priority patent/CN112286031B/zh
Application granted granted Critical
Publication of EP3599517B1 publication Critical patent/EP3599517B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • 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
    • 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
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • 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
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/32—Component parts or constructional details, e.g. collet, stud, virole or piton
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B19/00—Indicating the time by visual means
    • G04B19/06—Dials
    • G04B19/08—Geometrical arrangement of the graduations
    • G04B19/082—Geometrical arrangement of the graduations varying from the normal closed scale
    • 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
    • G04B45/00—Time pieces of which the indicating means or cases provoke special effects, e.g. aesthetic effects
    • G04B45/0038—Figures or parts thereof moved by the clockwork
    • G04B45/0061—Moving parts of the clockwork, e.g. pendulum, hands in special form, mostly constructed as a figure

Definitions

  • the invention relates to a timepiece movement comprising at least one regulating member which is a tourbillon or carousel comprising a cage, said movement comprising a drive mechanism comprising a fixed structure on which is mounted to pivot, around a main axis, a supporting arm of said cage, said arm being subjected to the return torque of a first source of energy, said drive mechanism further comprising at least one second source of energy, arranged to permanently supply said first source of energy; energy.
  • a timepiece movement comprising at least one regulating member which is a tourbillon or carousel comprising a cage, said movement comprising a drive mechanism comprising a fixed structure on which is mounted to pivot, around a main axis, a supporting arm of said cage, said arm being subjected to the return torque of a first source of energy, said drive mechanism further comprising at least one second source of energy, arranged to permanently supply said first source of energy; energy.
  • the invention also relates to a timepiece, in particular a watch, comprising such a movement.
  • the invention relates to the field of clockwork drive mechanisms, and the field of clockwork display mechanisms.
  • a bursting of the displays is also appreciated, and makes it possible to offer a new appearance of the dial or the mechanism.
  • Retrograde displays are generally limited to driving needles, or more rarely discs.
  • the document CH709331A2 on behalf of SEIKO INSTR. describes a display mechanism which includes a cage unit including an exhaust and a regulator, and an operating unit configured to differentiate the speed of movement of the cage unit with the passage of time and to move the cage unit in the direction approaching or away from a first axis which is the center of a particular display area, in which the operating unit moves the cage unit so that the path of motion, reproduced as the cage unit moves in the direction approaching the first axis which is the center of the particular display area, is continuous with the path of movement reproduced when the cage unit moves in the direction away from the first axis which is the center of the particular display area.
  • the invention proposes to develop a retrograde drive mechanism which is capable of carrying moving bodies of much greater inertia than needles, in particular tourbillons or the like, and therefore of proposing entirely new displays.
  • the invention relates to a timepiece movement according to claim 1.
  • the invention also relates to a timepiece, in particular a watch, comprising at least one such movement.
  • the invention relates to a clockwork movement 500 comprising at least one regulating member 15 which is a tourbillon or a carousel comprising a cage 150, and comprising a clockwork drive mechanism 100, which has the advantage of being able to be used. in a watch, or even in a static timepiece, with new functions.
  • This drive mechanism 100 comprises a structure 110, such as a plate, bridge or the like, on which is mounted an arm 1 pivoting about a main axis D0.
  • This arm 1 carries a first mechanism, which constitutes a satellite 10, which is mounted to pivot on the arm 1 about a first pivot axis D1, which is distant from the main axis D0.
  • This satellite 10 comprises a first wheel 11, which is mounted to pivot about the first pivot axis D1 or a secondary pivot axis D11 which is parallel to it.
  • the arm 1 is subjected to the return torque of a first energy source 12, such as a barrel, a weight system, or the like.
  • a first energy source 12 such as a barrel, a weight system, or the like.
  • the drive mechanism 100 also comprises at least one second energy source 22, which is arranged to subject a third mobile 3 that the drive mechanism 100 comprises to a return torque, directly or indirectly through a second. mobile 2 mounted to pivot around a second pivot axis D2, as in the particular and non-limiting variant illustrated by the figures 1 and 2 .
  • This second energy source 22 is the main energy source, and it is designed to store more energy than the first energy source 12.
  • the first wheel 11 is arranged to roll on the third mobile 3 in a rolling movement of regular advance, under the action of the return torque of the first energy source 12.
  • the satellite 10 thus constitutes a planetary mobile, which moves in rotation around the third mobile 3, around the main axis D0, always in the same direction, according to the arrow G (clockwise on the figure 1 ), and at constant speed.
  • the third mobile 3 is arranged to remain in a fixed position during a first elementary travel of the satellite 10, and to perform a rotation, and in particular a rapid rotation, always in one direction, that of the anti-clockwise B arrow on the figures 1 and 2 , during a second elementary course of the course of the satellite 10, under the action of the second energy source 22.
  • the first wheel 11 drives the cage 150 of the tourbillon or carousel, or constitutes the cage 150 of the tourbillon or carousel.
  • the arm 1 moves in the direction of the arrow E under the action of the first energy source 12 relative to the third mobile 3 when the latter is stationary, while that, during the return of the third mobile 3 under the action of the second energy source 22, the arm 1, which is carried by the third mobile 3, moves retrograde in the direction of the arrow F, with respect to to the fixed structure 110, during the second elementary travel of the satellite 10.
  • the axis D1 Due to the successive rotations of the arm in the first direction of advance according to arrow E, and according to the second reverse direction according to arrow F, the axis D1 performs a limited angular travel around the main axis D0.
  • the first elementary stroke of the satellite 10 is much greater than the second elementary stroke of the stroke, in particular more than twenty times greater than the latter.
  • the complete cycle lasts one minute, with fifty-eight seconds of slow-speed travel of arm 1 in the first elementary race, and two seconds of rapid return of arm 1 in the second elementary race.
  • the invention makes it possible to modulate the ratio between the first part of the race and the second elementary race of the race in a different way; it is for example conceivable to obtain a first elementary race and a second elementary race that are equal.
  • the drive mechanism 100 comprises stop means 120, which are fixed to the structure 110, and which are more particularly arranged to cooperate with complementary stop means 123 that the third mobile 3 comprises for its maintenance in position, or that comprises another external mobile meshing directly or indirectly with the third mobile 3.
  • the stop means 120 more particularly comprise a trigger lever, which is arranged to cooperate successively with pins distributed over the third mobile 3, and which constitute these additional stop means 123 in the non-limiting example illustrated by the figures 1 and 2 .
  • these pins are arranged angularly in a regular manner. It is nevertheless possible to design other angular spacings, to achieve particular displays.
  • These stopping means 120 are disengageable, under the action of clutch control means 13 which the arm 1 comprises, when the first wheel 11 ends its first elementary stroke, to allow the pivoting of the third mobile 3 in a single direction ( anti-clockwise arrow B) under the action of the second energy source 22 by causing a retrograde rotation of the arm 1 until the start of its angular travel.
  • the third mobile 3 When the third mobile 3 is stationary in an angular stop position, the first wheel 11 performs a first elementary stroke, and the arm 1 moves forward angularly at a slow speed which is its display speed. .
  • the clutch control means 13 disengage the stopping means 120, and the third mobile 3 is then free and subjected to the torque of the second energy source 22, directly or through the second mobile 2 depending on the construction variant chosen .
  • the third mobile 3 then performs a rotation, and more particularly a sudden and almost instantaneous rotation, before returning to another angular stop position between another pin 123 and the trigger lever 120. And this rotation of the third mobile 3 causes the return retrograde the arm 1 to its position of the start of angular travel, and in particular in the case illustrated at an accelerated speed which is much greater than its slow display speed.
  • the first wheel 11 is arranged to roll inside the third mobile 3.
  • Many other configurations can be envisaged, in particular concerning the relative positions of the various pivot axes, with cascades of suitable references.
  • the operation of the drive mechanism 100 is dependent on the level of energy available at the level of the second energy source 22.
  • the second energy source 22 is advantageously recharged by an automatic winding mechanism, not detailed here because it is well known to those skilled in the art: the first energy source 11 is permanently reset by the second energy source as long as the latter has sufficient 'energy, this first energy source 11 thus constitutes a buffer, and the drive of the satellite 10 by this first energy source 11 is thus a so-called constant force mechanism, or more precisely constant torque, until the end of the main barrel power reserve
  • the stop means 120 comprise a rocker, which forms a trigger lever, and which is pivotally mounted on a rocker axis D12, and which is biased in the direction of arrow D by elastic return means 127, such as spring or the like.
  • This rocker carries a rocker pin 129.
  • the arm 1 comprises a ramp 13, which is arranged to cooperate with the rocker pin 129, at the end of the angular advance travel of the arm 1, and to push the rocker back in the direction of arrow C, which makes it possible to eclipse a beak of the rocker comprising a bearing surface 128, which until then held in position a stop pin 123, which the third mobile 3 comprises (which includes three at 120 ° in this case).
  • the third mobile 3 is then released, and can rotate, its previously immobilized pin 123 being able to pass under the arm 1.
  • the position of the pins 123 directs the triggering, they guarantee the accuracy of the duration of a total running period.
  • the arm 1 comprises limiting means 20, which tend to oppose the engine torque of the first energy source 12, and which are arranged to limit the running speed of the first wheel 11.
  • limiting means 20 which tend to oppose the engine torque of the first energy source 12, and which are arranged to limit the running speed of the first wheel 11.
  • these limiting means 20 are braking and / or friction and / or regulation means. They can in particular include aerodynamic braking means, by eddy currents, or the like.
  • the first wheel 11 can carry a seconds hand.
  • the limiting means 20 are means for regulating the running speed of the first wheel 11 around the third mobile 3.
  • the regulating mechanism is preferably at the level of the satellite 10 which constitutes a planetary mobile.
  • the means for regulating the running speed of the first wheel 11 around the third mobile 3 comprise a stopper 17, such as an anchor or the like, and which is arranged to cooperate discontinuously with the first wheel 11, or with a mobile synchronous with the first wheel 11, or with a fourth mobile meshing directly or indirectly with the first wheel 11.
  • the second pivot axis D2 is parallel to the main axis D0 and distinct from it.
  • the third mobile 3 is arranged to pivot about the main axis D0.
  • the satellite 10 constitutes all or part of the limiting means 20, and is a regulator 15.
  • the regulating member 15 comprises at least one inertial mass 1700 subjected to a reciprocating pivoting movement by an anchor 170, which the stopper 17 comprises, and which is arranged to cooperate with a ratchet 18 driven directly or indirectly by the first wheel 11.
  • This anchor 170 makes it possible to limit the speed in order to avoid runaway, in particular during the rapid return in 2 seconds.
  • the ratchet 18 is coaxial with the first wheel 11.
  • this ratchet 18 is an escape wheel.
  • the first wheel 11 drives the tourbillon cage 150, or else constitutes the tourbillon cage 150.
  • the axis of the resonator mechanism typically a sprung balance, which the regulator member 15 comprises, coincides with the first pivot axis D1.
  • the first wheel 11 drives the carousel cage or constitutes the carousel cage.
  • the axis of the resonator mechanism typically a sprung balance, which the regulator member 15 comprises, is a secondary pivot axis, parallel to the first pivot axis D1, for example located at the distal end of a regulator 19 as illustrated on the figures 1 and 2 .
  • the regulator member 15 comprises a regulator 19, which is driven directly or indirectly by the first wheel 1.
  • this regulator 19 is synchronous with the first wheel 11, and is able to constitute a first display of a first time magnitude.
  • the regulator 19 is a tourbillon or carousel cage.
  • Each mobile of the movement drive mechanism according to the invention can be used for a particular display.
  • the arm 1 constitutes or drives a display of a second time magnitude.
  • This arm can carry eccentric displays, for example on stars mounted to pivot on the arm 1.
  • the third mobile 3 constitutes or drives a display of a third time magnitude, for example a minute display advancing by jumps.
  • the second mobile 2 constitutes or drives a power reserve display.
  • this drive mechanism specific to the invention allows a very lively display of the passage of time, by the very visible rolling of the first wheel 11 on the third mobile 3, and by the periodic retrograde return of the arm 1.
  • Each mobile can be used to carry an off-center display.
  • the invention also relates to a timepiece 1000 comprising at least one such timepiece movement 500, and which in a first variant is a watch.
  • first energy source 12 and / or its second energy source 22 may conventionally include at least one barrel, and / or an electromechanical energy source, or the like.
  • the second energy source 22 is recharged by an automatic winding mechanism.
  • the timepiece 1000 is static, and may in particular be a clock. Its first energy source 12 and / or its second energy source 22 may conventionally include at least one barrel, and / or an electromechanical energy source, or the like. Or again its first energy source 12 and / or its second energy source 22 comprises at least one weight, and this timepiece 1000 then comprises means for winding each weight. However, preferably the first energy source 12 is a cylinder forming a buffer, which means that only the second energy source 22 which supplies the first energy source 12 has to be wound up.
  • the principle of the invention is applicable to many other variants, and to many particular applications.
  • This principle is illustrated, in a simplified manner compared to figures 1 and 2 , by the figures 4 to 9 , which only include the first energy source 12, illustrated in the form of a simple flat spring, the arm 1 carrying the first wheel 11, and the third mobile 3 on which this first wheel 11 rotates.
  • a tourbillon cage carried by the first wheel 11, performs one revolution per minute, the first wheel 11 moves on the third mobile 3 for about 18 seconds when the third mobile 3 is still in the fixed position, and continues to roll on this third mobile during the two seconds that the retrograde return of 120 ° of the third mobile 3 in the counterclockwise direction in these figures lasts.
  • the figure 5 shows the assembly in position just after such a retrograde return; the figure 6 shows an intermediate position X; the figure 7 shows the extreme angular position of arm 1 in clockwise travel, and the figure 8 illustrates the retrograde return in an anti-clockwise direction of the third mobile (visible by the change in position of the marks 1, 2, 3) and of the arm 1 which it carries.
  • the figure 10 illustrates yet another variant, with an arm 1 forming a winding rake on a winding barrel of the cage arm, constituting the first energy source 12, which leads the arm 1 of the cage; under the effect of its torque, the tourbillon cage is driven and rotates around the circumference of the third mobile 3, the arm 1 moves as a function of the frequency and of the gear ratio.
  • the arm 1 leading the cage moves from its first position of 0 ° and reaches its maximum position 120 °.
  • the second energy source 22 here constituted by the barrel of the basic movement of a watch. This barrel is in chain with a reduction mobile 2230, and the latter in connection with the third mobile 3.
  • the force of the movement barrel 22 will lead the reduction mobile 2230 and in fact will lead the third mobile 3 in anti- rotation. hourly 120 °.
  • the movement in degrees of the third mobile 3 is managed via a gear train 221 and positioned by a stop pin at the level of a position lock 223, this gear 221 can be linked either to the reduction mobile 2230, or with the movement barrel 22.
  • a regulator with inverter comprising in particular a pinion, a ratchet 18, an anchor 170, is in series with the third mobile 3, and makes it possible to '' adjust the duration of the retrograde return, in particular between 1 and 10 seconds.
  • the first energy source 12 here the spring of the cage arm
  • the cage continues to operate by moving around the circumference of the third mobile 3.
  • This variant of the figure 10 allows the angular travel to be managed other than by pins 123 of the variant of figures 1 and 2 , which the position gear 221 replaces here, it is here possible to manage other angular values, for example 360 ° to display a passage of date, or the like.
  • the first energy source 12 here the spring of the cage arm, has a pre-winding giving the torque necessary for the operation of the tourbillon, this force will remain constant.
  • the angular travel of 120 ° in anti-clockwise rotation of the third mobile 3 regularly arms the cage arm spring.
  • This arrangement also makes it possible to correct the moon directly via the crown, it is no longer necessary to integrate a corrector integrated into the middle part.
  • the invention provides an almost constant driving force to the regulating mechanism, in particular a tourbillon or carousel cage, throughout the power reserve of the main barrel.
  • the figures 11 to 14 illustrate the wide latitude offered by the invention for the positioning of the various displays.
  • the hours and minutes are read on a dial at 12 o'clock, that of the power reserve on a sector with retrograde hand at 9 o'clock, that of the moon and / or day / night display, or sunset, or other, at 3 o'clock, while the tourbillon has a displacement of 120 °, and it is possible to orient the displacement of the cage over 120 ° according to a substantially peripheral movement as on the figures 11 and 14 , or according to a movement around an axis eccentric to the maximum as on the figures 12 and 13 , with a retrograde movement of the cage respectively from left to right, or from right to left.
  • the value of 120 ° taken for the examples is in no way binding, the angular value depends on the desired hourly travel time, the value of the retrograde travel is also adjustable, for example between 2 and 5 seconds, and makes it possible to obtain a non-abrupt, shock-free retrograde feedback.
  • the retrograde return is not linked to the frequency of the resonator mechanism, and has no influence on the rate of the movement.
  • the third mobile it is possible to equip the third mobile with several satellites 10 on its periphery. It is also possible to design a system on several floors to handle separate functions.
  • the figures 15 to 31 illustrate, on the basic principle of figure 10 , a particular embodiment of the invention, in which the first wheel 11 is a tourbillon cage 150, and where the third mobile 3 is a mobile with no cage 700, which will be detailed below.
  • the clockwork movement 500 comprises, for controlling the retrograde movement of the retrograde pivoting arm 1, a very compact mechanism which comprises a mobile trigger 600 kinematically connected to the second energy source 22, and which is arranged to cooperate with a cam movable 620 kinematically connected to the arm 1 connected to the first energy source 12.
  • This clockwork movement 500 comprises at least one regulating member which is a tourbillon or carousel comprising a cage 150.
  • the movement 500 comprises a drive mechanism 100 comprising a fixed structure 110 on which is mounted to pivot, around a main axis. D0, an arm 1 carrying the cage 150. This arm 1 is subjected to the return torque of a first energy source 12.
  • the drive mechanism 100 further comprises at least one second energy source 22, arranged for continuously replenish the first energy source 12.
  • the second energy source 22 is arranged to drive a cage-pitch mobile 700, which itself drives a cage pinion 710 for driving the cage 150 in rotation.
  • the movement 500 comprises, for the periodic control of a retrograde movement of the arm 1, a mobile trigger 600 kinematically connected to the second energy source 22 and always rotating in the same direction, and which is arranged to cooperate, at the level of a pallet 601 which the mobile trigger 600 comprises, with a cam 621 which comprises a mobile cam 620 kinematically connected to the arm 1.
  • This cam 621 covers an angular sector less than 360 ° and which corresponds to an advance movement of the arm 1 by pivoting in a first direct direction E at a first constant speed relative to the fixed structure 110 as long as the pallet 601 is resting on cam 621.
  • An interruption of the cam 621 is arranged to trigger a fall of the pallet 601 of the mobile trigger 600 under the action of the driving torque of the second energy source 22, and to control a rapid retrograde return of the arm 1 in a second retrograde direction F relative to the fixed structure 110 at a second speed greater than the first speed, during the fall of the pallet 601 between the moment when it leaves the cam 621 and the moment when it comes back to bear on the cam 621, the mobile cam 620 performing, during the fall, a retrograde pivoting under the effect of the retrograde return of the arm 1.
  • the mechanism according to the invention thus comprises two branches, one supplied by the first energy source 12, the other by the second energy source 22, and the point of convergence of these two branches is the cooperation zone. between the trigger mobile 600 and the cam mobile 620.
  • This cooperation is periodic, because its period is determined by the oscillator of the tourbillon, in particular a sprung balance or the like.
  • the retrograde pivoting arm 1 is here pivoted on the plate or on a structure 110 that the movement 500 comprises.
  • the first energy source 12 comprises here, without limitation, at least one cage arm spring 120, fixed to a first end. to the retrograde pivoting arm 1, and to the plate or the structure 110 at its other end; in the figures, and in a nonlimiting manner, this cage arm spring 120 is a spiral spring.
  • the cage-pitch mobile 700 comprising the first lower wheel 680 and the second intermediate wheel 670 is blocked or released depending on the relative position of the trigger mobile 600 and the cam mobile 620, as will be explained below.
  • This cage pitch mobile 700 constitutes a SIAM 120 ° pitch wheel (counterclockwise).
  • the retrograde pivoting arm 1 carries a fixed tourbillon wheel 720, with which cooperates the pinion of an escape wheel of an escape mechanism not detailed here because it is conventional, for example a Swiss lever escapement cooperating with a balance wheel. spiral not shown in the figures where only the escape wheel is visible. In particular, but not limited to, the imposed frequency is one cage rotation per minute.
  • the retrograde pivoting arm 1 can only travel an angular travel of at most 120 ° in one minute, corresponding to a complete revolution of the cage: in a direct direction for approximately fifty-eight seconds of travel at speed slow of arm 1 in the first elementary race, and about two seconds of rapid return in a retrograde direction of arm 1 in the second elementary race.
  • the toothed sector 660 meshes, directly or indirectly as in the figures, with a cam mobile 620, which therefore undergoes direct or retrograde movements like the retrograde pivoting arm 1: when the retrograde pivoting arm 1 pivots in the direct direction E, the cam mobile 620 pivots in a direct direction H, and, when the retrograde pivoting arm 1 pivots in the retrograde direction F, the cam mobile 620 pivots in a retrograde direction J.
  • the toothed sector 660 engages indirectly with the cam mobile 620 through a gear train, which is not limited to illustrated here by a first gear 630 and a second gear 640 carrying a pinion 650.
  • this cam train comprises at least one component that can be adjusted by friction or the like: for example, the second transmission 640 may include two lanterned carriageways cooperating by friction with each other for fine adjustment in the factory or in the after-sales service of the angular orientation of the pinion. upper 650 with respect to the other lower toothing carried by this second reference 640, to adjust if necessary the retrograde angle of 120 °, or the like.
  • This mobile cam 620 comprises or carries a cam 621, which covers an angular sector less than 360 ° and which corresponds to an advance movement of the retrograde pivoting arm 1, the interruption of the cam 621 being arranged to trigger a fall of 'a pallet 611 which the mobile trigger 600 comprises, and for controlling a rapid retrograde return of the retrograde pivoting arm 1.
  • This cam movable 620 has alternating rotations in both directions, according to the direction of angular movement of the retrograde pivoting arm 1.
  • this cam 621 is a linear torque cam, with a track coaxial with the axis of the cam movable 620.
  • This cam 621 covers an angular sector less than 360 °, chosen according to the desired kinematics, and is extended. by a clearance 623.
  • the cam 621 has a cam tip 622 at one of its ends.
  • the track of the cam 621 is cylindrical, it will be understood that its profile could be other than circular, without altering its function of animating the retrograde mechanism.
  • the use of another profile, with a cam of particular shape, allows specific operations of the displays, for example to avoid certain areas, at the cost of a slight energy consumption.
  • the second energy source 22 comprises here, without limitation, at least one main barrel, which is recharged with energy by known means, the figures illustrate more particularly and without limitation a single main barrel 22, reset through a gear train. winding, not detailed here, by a time-setting and winding rod 2200, arranged to be actuated by the crown 220.
  • this second energy source 22 can be of any kind customary in watchmaking, for example a electrical source capable of driving a rotating mobile, or the like.
  • This main barrel 22 here conventionally drives a finishing gear train, which comprises a large average mobile 601, and a small average mobile 602. The latter drives a finishing wheel 603.
  • the second energy source 22 drives, through the finishing gear, the finishing mobile 603, which drives a trigger mobile 600, which always turns in the same direction.
  • This trigger mobile 600 comprises a wheel of the trigger finger 610, which meshes with the finishing mobile 603. As seen in particular on the figure. figure 30 , this trigger finger wheel 610 is mounted coaxially, around an axis 619, with a trigger finger 615 carrying a pallet 611.
  • the wheel of the trigger finger 610 and the trigger finger 615 have a small angular mobility of angle ⁇ with respect to one another, of the order of a few degrees, and in particular of less than 15 degrees.
  • the wheel of the trigger finger 610 carries or comprises a spring arm 612, a distal end of which forming a hammer 613 is arranged to cooperate in abutment bearing with a pin 614 which the trigger finger 615 carries.
  • the wheel of the trigger finger 615. 610 comprises, on the one hand, a rear abutment surface 618 to limit the relative angular travel of the pin 614, and on the other hand a front abutment surface 617 to limit the angular travel of the hammer 613.
  • the spring arm 612 is here in one piece with the wheel of the trigger finger 610 and is movable in a slot 6120 that the latter comprises, and whose interior surfaces limit the radial travel of the spring arm 612; the spring arm 612 can, again, be an attached element, the radial travel of which is then limited by stop surfaces provided for this purpose.
  • the whole of the trigger mobile 600 is a single-piece component.
  • the track of the cam 621 is provided to act as a support for the pallet 611 of the trigger finger 610: as long as the pallet 611 is resting on the track of the cam 621, the pivoting arm retrograde 1 is driven by a regular forward movement in the direct direction, until the tip of the pallet 611 comes to rest on the cam point 622, the last moment before the fall of the pallet 611:
  • the release 623 of the cam wheel 620 is provided to allow, without hindering it, the passage of the pallet 611 along the cam movable 620: when the tip of the pallet 611 leaves the cam tip 622, the pallet 611 drops and performs a rapid movement under the driving effect of the finishing gear, this rapid movement begins with the passage of the pallet 611 in the clearance 623, then the pallet 611 leaves the grip of the cam mobile 620, and the wheel of the trigger finger 610 tends to make a complete turn around its axis, up to the ret Our support of the pallet 611 on the track of the cam 621
  • This cam 621 has also rotated in the meantime. Indeed, during the separation of the pallet 611 and the cam 621, nothing retains the cam wheel 620, nor consequently the retrograde pivoting arm 1 which is returned in rapid retrograde movement under the action of the arm spring. cage 120, and of course the cam wheel 620 also performs such a retrograde movement for about 2 seconds.
  • a regulator moving body 604 comprising for example a star meshing with the finishing mobile 603 and cooperating with a regulator anchor 605.
  • the second intermediate wheel 670 of the cage-pitch mobile 700 meshes with a cage pinion 710 which drives the cage 150, as can be seen on the figure. figure 22 .
  • This same figure 22 also shows the engagement between a reference 690, with which the trigger mobile 600 engages, with the first lower wheel 680 of the cage-pitch mobile 700.
  • the cage-pitch mobile 700 which is independent of the retrograde pivoting arm 1, rotates, and thus drives the tourbillon cage, until the end of the fall, and the cage-pitch mobile. 700 is then stopped.
  • the tourbillon cage continued to rotate, always in the same direction and at the same speed, for the duration of the fall.
  • the cam wheel 620 is driven in its retrograde direction J, and, at the end of the fall, is in an angular position in which the cam 621 receives the pallet 611 in radial support.
  • the cam wheel 620 has a periodically triggered reciprocating movement, the period of which depends on the frequency of the oscillator of the tourbillon.
  • the two energy sources have different functions: the main barrel of the movement 500, which is here the second energy source 22, defines the power reserve, supplies the system, but does not supply power. the live resonator; while the first energy source 12 here constituted by the cage spring 120 (which could also be a barrel, or the like), drives the cam mobile 620 carrying the cam 621, in this particular example controls the winding / disarming by 120 °, feeds the oscillator, and performs the movements + 120 ° and -120 °; the second energy source 22 continuously replenishes the first energy source 12._
  • the operation of the mechanism is thus ensured by short kinematic chains, comprising few components, which are easy and economical to execute.
  • the invention makes it possible to realize an innovative complication with low consumption of space in the watch case.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Transmission Devices (AREA)
  • Electromechanical Clocks (AREA)
  • Toys (AREA)
  • Measurement Of Unknown Time Intervals (AREA)

Claims (13)

  1. Uhrwerk (500), das mindestens ein regelndes Organ beinhaltet, das ein Tourbillon oder Karussel ist, das ein Rohwerk (150) beinhaltet, wobei das Uhrwerk (500) einen Antriebsmechanismus (100) beinhaltet, der eine feste Struktur (110) beinhaltet, auf der, um eine Hauptachse (D0) drehbar ein Trägerarm (1) des Rohwerks (150) montiert ist, wobei der Arm (1) dem Rückzugsmoment einer ersten Energiequelle (12) ausgesetzt ist, wobei der Antriebsmechanismus (100) weiter mindestens eine zweite Energiequelle (22) beinhaltet, die angeordnet ist, um die erste Energiequelle (12) ständig neu zu versorgen, wobei die zweite Energiequelle (22) angeordnet ist, um ein Drehteil einer Rohwerkteilung (700) anzutreiben, die selbst einen Rohwerktrieb (710) zum drehenden Antreiben des Rohwerks (150) antreibt, wobei das Uhrwerk (500) zur periodischen Steuerung einer rückläufigen Bewegung des Armes (1) ein Auslösedrehteil (600) beinhaltet, das kinematisch mit der zweiten Energiequelle (22) verbunden ist, und sich immer in dieselbe Richtung dreht, und das angeordnet ist, um im Bereich einer Palette (601), die das Auslösedrehteil (600) beinhaltet, mit einer Kurvenscheibe (621) zusammenzuwirken, die ein Kurvenscheibendrehteil (620) beinhaltet, das kinematisch mit dem Arm (1) verbunden ist, wobei die Kurvenscheibe (621) einen Winkelsektor kleiner als 360° abdeckt, und die einer Vorgangbewegung des Armes (1) in einer ersten direkten Richtung E mit einer ersten konstanten Geschwindigkeit in Bezug auf die feste Struktur (110) drehend, solange entspricht, wie die Palette (601) an der Kurvenscheibe (621) anliegt, wobei eine Unterbrechung der Kurvenscheibe (621) angeordnet ist, um einen Fall einer Palette (601), die das Auslösedrehteil (600) beinhaltet, unter Wirkung eines Triebkräftepaares der zweiten Energiequelle (22) auszulösen, und um eine rasche rückläufige Rückkehr des Armes (1) in eine zweite rückläufige Richtung F in Bezug auf die feste Struktur (110), mit einer zweiten Geschwindigkeit, die größer als die erste Geschwindigkeit ist, während des Falls der Palette (601) zwischen dem Zeitpunkt, wo sie die Kurvenscheibe (621) verlässt, und dem Zeitpunkt, wo sie auf Anlage zur Kurvenscheibe (621) zurückkehrt, zu steuern, wobei das Kurvenscheibendrehteil (620) während des Falles eine rückläufige Zapfendreherei unter der Wirkung der rückläufigen Rückkehr des Armes (1) durchführt.
  2. Uhrwerk (500) nach Anspruch 1, dadurch gekennzeichnet, dass das Auslösedrehteil (600) ein Rad des Auslösefingers (610) beinhaltet, welches mit einem Drehteil (603) eines Finissage-Räderwerks eingreift, das durch die zweite Energiequelle (22) versorgt wird, und das koaxial um eine Achse (619) mit einem Auslösefinger (615), Träger der Palette (611), montiert ist, und dadurch, dass das Rad des Auslösefingers (610) und der Auslösefinger (615) eine Winkelbeweglichkeit α zueinander aufweisen, die kleiner als 15 Grad ist.
  3. Uhrwerk (500) nach Anspruch 2, dadurch gekennzeichnet, dass das Rad des Auslösefingers (610) einen Federarm (612) trägt oder beinhaltet, von dem ein distales Ende, das einen Hammer (613) bildet, angeordnet ist, um auf Anschlag anliegend mit einem Sperrstift (614) zusammenzuwirken, den der Auslösefinger (615) trägt, und dadurch, dass das Rad des Auslösefingers (610) einerseits eine hintere Anschlagoberfläche (618) zum Begrenzen des relativen Winkelweges des Sperrstiftes (614), und andererseits eine vordere Anschlagoberfläche (617) zum Begrenzen des relativen Winkelweges des Hammers (613) beinhaltet.
  4. Uhrwerk (500) nach Anspruch 3, dadurch gekennzeichnet, dass der Federarm (612) in einem Stück mit dem Rad des Auslösefingers (610) ist und in einem Langloch (6120) beweglich ist, das dieser letztere beinhaltet, und dessen Innenflächen den radialen Weg des Federarms (612) begrenzen.
  5. Uhrwerk (500) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass das gesamte Auslösedrehteil (600) eine einstückige Komponente ist.
  6. Uhrwerk (500) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Drehteil einer Rohwerkteilung (700) ein erstes unteres Rad (680) und ein zweites Zwischenrad (670) beinhaltet, die axial besabstandet und drehverbunden sind, und die auch koaxial und axial von einem gezahnten Sektor (660) oder einer vollständigen Zahnung beabstandet sind, die der sich rückläufig drehende Arm (1) beinhaltet, wobei das zweite Zwischenrad (670) mit dem Rohwerktrieb (710) eingreift, und das erste untere Rad (680) mit einem Vorgelege (690) eingreift, mit dem das Auslösedrehteil (600) eingreift.
  7. Uhrwerk (1000), nach Anspruch 6, dadurch gekennzeichnet, dass der gezahnte Sektor (660) oder die vollständige Zahnung, die der sich rückläufig drehende Arm (1) beinhaltet, indirekt mit dem Kurvenscheibendrehteil (620) durch ein Kurvenscheibenräderwerk hindurch eingreift, das mindestens ein Vorgelege (640) beinhaltet, das zwei gekerbte Minutenrohre beinhaltet, die durch Reibung zueinander für eine Feineinstellung der Ausrichtung des rückläufigen Winkels des Armes (1) zusammenwirken.
  8. Uhrwerk (500) nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der rückläufige Dreharm (1) ein festes Rad (720) eines Tourbillons trägt, mit dem der Trieb eines Hemmungsrades eines Hemmungsmechanismus zusammenwirkt, der mit einer Spiralunruh zusammenwirkt, die das Uhrwerk (500) beinhaltet.
  9. Uhrwerk (500) nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Fall der Palette (601) und die Geschwindigkeit der Drehteile und des Auslösedrehteils (600) durch ein Regelungsdrehteil (604) begrenzt ist, das einen Stern beinhaltet, der mit einem Drehteil (603) eines Finissage-Räderwerks eingreift, das durch die zweite Energiequelle (22) versorgt wird, und mit dem Regelungsanker (605) zusammenwirkt.
  10. Uhrwerk (500) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass das Drehteil einer Rohwerkteilung (700) um die Hauptachse (D0) herum koaxial mit der ersten Energiequelle (12) ist.
  11. Uhrwerk (500) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass ein Block, bestehend aus dem rückläufigen Dreharm (1) und dem Drehteil einer Rohwerkteilung (700), von der ersten Energiequelle (11) getrennt ist, die auf die feste Struktur (110) ausgelagert ist, und die ein erstes Rad (1200) beinhaltet, das mit einem Rohwerkarmfeder (120) zusammenwirkt, die die erste Energiequelle (12) beinhaltet, und die mit einem gezahnten Sektor (660) oder der vollständigen Zahnung eingreift, die der sich rückläufig drehend Arm (1) beinhaltet.
  12. Uhrmachereistück (1000), das mindestens ein Uhrwerk (500) nach einem der Ansprüche 1 bis 11 beinhaltet.
  13. Uhrmachereistück (1000) nach Anspruch 12, dadurch gekennzeichnet, dass es eine Uhr ist, und dadurch, dass die erste Energiequelle (12) und/oder die zweite Energiequelle (22) ein Federhaus ist.
EP19187588.9A 2018-07-24 2019-07-22 Retrogrades tourbillon oder karussell eines uhrwerks Active EP3599517B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US16/912,183 US11493884B2 (en) 2018-07-24 2020-06-25 Timepiece retrograde tourbillon or karussel
JP2020121197A JP7063949B2 (ja) 2018-07-24 2020-07-15 計時器の逆行するツールビロンまたはカルーセル
RU2020123925A RU2742378C1 (ru) 2018-07-24 2020-07-20 Часовой ретроградный турбийон или карусель
CN202010710207.3A CN112286031B (zh) 2018-07-24 2020-07-22 钟表机芯和包括钟表机芯的钟表

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18185166.8A EP3599515B1 (de) 2018-07-24 2018-07-24 Antriebsmechanismus für uhrwerk
EP18185167.6A EP3599516B1 (de) 2018-07-24 2018-07-24 Retrogrades tourbillon oder karussell eines uhrwerks

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EP3599517A1 EP3599517A1 (de) 2020-01-29
EP3599517B1 true EP3599517B1 (de) 2021-03-10

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EP3599516B1 (de) * 2018-07-24 2024-04-03 Harry Winston SA Retrogrades tourbillon oder karussell eines uhrwerks

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CN112286031B (zh) 2022-03-29
JP7063949B2 (ja) 2022-05-09
JP2021018250A (ja) 2021-02-15
EP3599517A1 (de) 2020-01-29
US11493884B2 (en) 2022-11-08
CN112286031A (zh) 2021-01-29
RU2742378C1 (ru) 2021-02-05
US20210026304A1 (en) 2021-01-28

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