EP3599517A1 - Retrogrades tourbillon oder karussell eines uhrwerks - Google Patents

Retrogrades tourbillon oder karussell eines uhrwerks Download PDF

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Publication number
EP3599517A1
EP3599517A1 EP19187588.9A EP19187588A EP3599517A1 EP 3599517 A1 EP3599517 A1 EP 3599517A1 EP 19187588 A EP19187588 A EP 19187588A EP 3599517 A1 EP3599517 A1 EP 3599517A1
Authority
EP
European Patent Office
Prior art keywords
mobile
arm
cage
cam
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.)
Granted
Application number
EP19187588.9A
Other languages
English (en)
French (fr)
Other versions
EP3599517B1 (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 EP18185167.6A external-priority patent/EP3599516B1/de
Priority claimed from EP18185166.8A external-priority patent/EP3599515B1/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
    • 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
    • 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 pivotally mounted, around a main axis, an arm carrying said cage, said arm being subjected to the return torque of a first energy source, said drive mechanism further comprising at least a second energy source, arranged to permanently replenish 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.
  • Lovers of horological complications are sensitive to a certain animation of the displays of a timepiece, which can be achieved by retrograde display mechanisms, or by tourbillon mechanisms or the like, which in addition guarantee better insensitivity to the positions. .
  • a bursting of the displays is also appreciated, and makes it possible to offer a new physiognomy 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 comprises a cage unit comprising 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 moving 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 movement path, reproduced when 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 mobiles of much greater inertia than needles, in particular vortices 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 in a static timepiece, with new features.
  • 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 pivotally mounted on the arm 1 around a first pivot axis D1, which is distant from the main axis D0.
  • This satellite 10 comprises a first wheel 11, which is pivotally mounted around 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 a second energy source 22, which is arranged to subject a third mobile 3 to a restoring torque 3 which the drive mechanism 100 includes, directly or indirectly through a second mobile 2 mounted pivoting 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 arranged 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 regular advance rolling movement, under the action of the restoring torque of the first energy source 12.
  • the satellite 10 thus constitutes a planetary mobile, which rotates 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 stroke of the satellite 10, and to perform a rotation, and in particular a rapid rotation, always in one direction, that of the anti-clockwise arrow B on the figures 1 and 2 , during a second elementary race of the race 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 stopped, while that, when the third mobile 3 is recalled 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 race of the satellite 10.
  • the axis D1 Due to the successive rotations of the arm in the first direction of advance along the arrow E, and in the second reverse direction along the arrow F, the axis D1 performs a limited angular travel around the main axis D0.
  • the first elementary race of the satellite 10 is much greater than the second elementary race of the race, 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 however makes it possible to otherwise modulate the ratio between the first part of the race and the second elementary race of the race, it is for example imaginable to obtain a first elementary race and a second elementary race equal.
  • the drive mechanism 100 includes stop means 120, which are fixed to the structure 110, and which are more particularly arranged to cooperate with complementary stop means 123 that includes the third mobile 3 for maintaining it in position, or that includes another external mobile engaging 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 on the third mobile 3, and which constitute these complementary stop means 123 in the nonlimiting 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 produce particular displays.
  • stop means 120 are disengageable, under the action of declutching control means 13 that comprises the arm 1, 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 stopped in an angular stop position, the first wheel 11 performs a first elementary stroke, and the arm 1 moves in angular stroke in advance at a slow speed which is its display speed .
  • the declutching control means 13 disengage the stop 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 selected .
  • the third mobile 3 then performs a rotation, and more particularly a sudden and almost instantaneous rotation, before returning to another angular abutment position between another pin 123 and the trigger lever 120. And this rotation of the third mobile 3 causes the return retrograde of the arm 1 to its angular start position, and in particular in the case illustrated at an accelerated speed which is much higher than its slow display speed.
  • the first wheel 11 is arranged to roll inside the third mobile 3.
  • Many other configurations are possible, in particular concerning the relative positions of the different pivot axes, with cascades of suitable references.
  • the third mobile 3 to the torque of at least one third energy source, for example in direct engagement.
  • the operation of the drive mechanism 100 is dependent on the level of energy available at the second energy source 22.
  • the second energy source 22 is advantageously recharged by an automatic winding mechanism, not detailed here as 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 satellite 10 by this first energy source 11 is thus a mechanism known as constant force, 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 returned in the direction of the arrow D by elastic return means 127, such as spring or similar.
  • 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 for push the rocker 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 maintained in position a stop pin 123, which comprises the third mobile 3 (which includes three at 120 ° in the present case).
  • the third mobile 3 is then released, and can rotate, its pin 123 previously immobilized being able to pass under the arm 1.
  • the position of the pins 123 directs the triggering, they guarantee the precision of the duration of a period of total travel.
  • the arm 1 comprises limiting means 20, which tend to oppose the driving 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 driving 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 may in particular include aerodynamic braking means, by eddy currents, or the like.
  • the first wheel 11 can carry a second 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 retainer 17, such as an anchor or the like, and which is arranged to cooperate discontinuously with the first wheel 11, or with a synchronous mobile of the first wheel 11, or with a fourth mobile engaging 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 around the main axis D0.
  • the satellite 10 constitutes all or part of the limiting means 20, and is a regulating member 15.
  • the regulating member 15 comprises at least one inertial mass 1700 subjected to an alternating pivoting movement by an anchor 170, which comprises the retainer 17, 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 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 cage 150 of the vortex, or else constitutes the cage 150 of the vortex.
  • the axis of the resonator mechanism typically a balance-spring, which comprises the regulating member 15, coincides with the first pivot axis D1.
  • the axis of the resonator mechanism typically a balance-spring, which comprises the regulating member 15, 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 regulating 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 capable of constituting a first display of a first time quantity.
  • 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 temporal magnitude.
  • This arm can carry eccentric displays, for example on stars pivotally mounted on the arm 1.
  • the third mobile 3 constitutes or drives a display of a third temporal magnitude, for example a display of the minutes advancing by jumps.
  • the second mobile 2 constitutes or drives a power reserve 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 can conventionally comprise at least one barrel, and / or an electromechanical, or other, energy source.
  • the second energy source 22 is recharged by an automatic winding mechanism.
  • the timepiece 1000 is static, and may in particular be a pendulum.
  • Its first energy source 12 and / or its second energy source 22 can conventionally comprise at least one barrel, and / or an electromechanical, or other, energy source.
  • 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.
  • the first energy source 12 is a buffer barrel, which means that only the second energy source 22 which feeds the first energy source 12 has to be raised.
  • FIG. 1 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 figures 4 to 9 , which comprise only 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 turns 11.
  • a tourbillon carriage carried by the first wheel 11, makes one revolution per minute, the first wheel 11 moves on the third mobile 3 for approximately 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 ° lasts from the third mobile 3 counterclockwise in these figures.
  • 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 time travel, and the figure 8 illustrates the retrograde counterclockwise return of the third mobile (visible by the change in position of the pins 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 rotated 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 initial position by 0 ° and arrives at its maximum position 120 °.
  • the second energy source 22 is unlocked, 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 drive the reduction mobile 2230 and in fact will lead the third mobile 3 in anti-rotation 120 ° hourly.
  • the displacement 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 train 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 allows d '' 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, rearms
  • the cage continues to operate by moving around the circumference of the third mobile 3.
  • the first energy source 12 here the spring of the cage arm, has a pre-arm giving the torque necessary for the operation of the tourbillon, this force will remain constant.
  • the angular travel of 120 ° in counterclockwise rotation of the third mobile 3 regularly arms the cage arm spring.
  • This arrangement also makes it possible to make the correction of the moon directly by the crown, it is no longer necessary to integrate a corrector integrated into the middle.
  • 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 even sunset, or other, at 3 o'clock, while the tourbillon has a movement over 120 °, and it is possible to orient the movement of the cage over 120 ° according to a substantially peripheral movement as on the Figures 11 and 14 , or according to a movement around a maximum eccentric axis 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 duration of the desired hourly stroke, the value of the retrograde stroke is also adjustable, for example between 2 and 5 seconds, and allows obtain an abrupt retrograde return, devoid of shock.
  • the retrograde return is not linked to the frequency of the resonator mechanism, and has no influence on 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 multi-stage system to manage separate functions.
  • FIGS 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 a cage pitch 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 trigger mobile 600 kinematically connected to the second energy source 22, and which is arranged to cooperate with a cam mobile 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 pivotally mounted, 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 also comprises at least a second energy source 22, arranged for permanently 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 triggering mobile 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 that comprises the trigger mobile 600, with a cam 621 that comprises a cam mobile 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 in 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 pressing on cam 621.
  • An interruption of the cam 621 is arranged to trigger a fall of the pallet 601 of the triggering mobile 600 under the action of the engine torque of the second energy source 22, and to command 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 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, since its period is determined by the oscillator of the tourbillon, in particular a balance-spring or the like.
  • the retrograde pivoting arm 1 is here pivoted on the plate or on a structure 110 which comprises the movement 500.
  • the first energy source 12 here comprises, without limitation, at least one cage arm spring 120, fixed at 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 without limitation, 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 pitch wheel of 120 ° SIAM (anticlockwise).
  • the retrograde pivoting arm 1 carries a fixed tourbillon wheel 720, with which the pinion of an escape wheel of an escape mechanism cooperates, which is not detailed here because it is conventional, for example a Swiss anchor escapement cooperating with a balance wheel. hairspring not shown in the figures where only the escape wheel is visible. In particular but not limited to the imposed frequency is one rotation of the cage per minute.
  • the retrograde pivoting arm 1 can only travel an angular travel of maximum 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 stroke, and approximately two seconds of rapid return in a retrograde direction of arm 1 in the second elementary stroke.
  • 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, the cam mobile 620 pivots in a retrograde direction J.
  • the toothed sector 660 meshes indirectly with the cam mobile 620 through a gear train, which is non-limitatively illustrated here by a first reference 630 and a second reference 640 carrying a pinion 650.
  • this cam train comprises at least one component adjustable by friction or the like: for example, the second reference 640 may comprise two lanterned carriageways cooperating by friction with one another for fine adjustment in the factory or in 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 cam mobile 620 comprises or carries a cam 621, which covers an angular sector of less than 360 ° and which corresponds to a forward movement of the retrograde pivoting arm 1, the interruption of the cam 621 being arranged to trigger a fall d 'a pallet 611 that includes the trigger mobile 600, and for controlling a rapid retrograde return of the retrograde pivoting arm 1.
  • This cam mobile 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 cam with linear torque, with a track coaxial with the axis of the cam mobile 620.
  • This cam 621 covers an angular sector less than 360 °, chosen as a function of 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 is understood that its profile could be other than circular, without altering its function of animation of the retrograde mechanism.
  • the use of another profile, with a cam of particular shape, allows particular operations of the displays, for example to avoid certain areas, at the cost of a slight consumption of energy.
  • the second energy source 22 here includes, without limitation, at least one main cylinder, which is recharged with energy by known means, the figures illustrate more particularly and without limitation a single main cylinder 22, rearmed 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 source of energy 22 can be of any kind customary in watchmaking, for example a electrical source capable of driving a mobile in rotation, or other.
  • This main barrel 22 conventionally drives a finishing train here, which comprises a large medium mobile 601, and a small medium mobile 602. The latter drives a finishing mobile 603.
  • the second energy source 22 drives, through the gear train, the finishing mobile 603, which drives a trigger mobile 600, which always turns in the same direction.
  • This trigger mobile 600 comprises a trigger finger wheel 610, which meshes with the finishing mobile 603. As visible in particular on the figure 30 , this wheel of the trigger finger 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 ⁇ from one relative to the other, 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, one distal end of which forms a hammer 613 is arranged to cooperate in abutment support with a pin 614 which the trigger finger 615 carries.
  • the wheel of the trigger finger 610 comprises, on the one hand a rear abutment surface 618 for limiting the relative angular travel of the pin 614, and on the other hand a front abutment surface 617 for limiting the angular travel of the hammer 613.
  • the spring arm 612 is here monobloc with the wheel of the trigger finger 610 and is movable in a light 6120 which the latter comprises, and whose internal surfaces limit the radial stroke of the spring arm 612; the spring arm 612 can also be an added element, the radial stroke of which is then limited by abutment surfaces provided for this purpose.
  • the entire trigger mobile 600 is a one-piece component.
  • the track of the cam 621 is provided to serve as a support for the pallet 611 of the trigger finger 610: as long as the pallet 611 is in abutment on the track of the cam 621, the pivoting arm retrograde 1 is animated with a regular forward movement in the direct direction, until the tip of the pallet 611 comes to bear on the cam tip 622, last instant preceding the fall of the pallet 611:
  • the release 623 of the cam wheel 620 is provided to allow, without obstructing it, the passage of the pallet 611 along the cam mobile 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 train, 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 full turn around its axis e, until the pallet 611 returns to bear on the track of the cam 6
  • This cam 621 has also rotated in the meantime. Indeed, during the separation of the pallet 611 and the cam 621, nothing more 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 mobile 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 visible on the figure 22 .
  • This same figure 22 still shows the meshing between a reference 690, with which the trigger mobile 600 meshes, 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 its rotation, always in the same direction and at the same speed, during 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 in the pallet 611 in radial support.
  • the cam wheel 620 has an alternating movement with periodic triggering, the period of which depends on the frequency of the oscillator of the vortex.
  • 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 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 arming / 120 ° disarm, powers the oscillator, and performs 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 produce an innovative complication with a low consumption of space in the watch case

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Transmission Devices (AREA)
  • Electromechanical Clocks (AREA)
  • Toys (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
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
EP18185167.6A EP3599516B1 (de) 2018-07-24 2018-07-24 Retrogrades tourbillon oder karussell eines uhrwerks
EP18185166.8A EP3599515B1 (de) 2018-07-24 2018-07-24 Antriebsmechanismus für uhrwerk

Publications (2)

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

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EP19187588.9A Active EP3599517B1 (de) 2018-07-24 2019-07-22 Retrogrades tourbillon oder karussell eines uhrwerks

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US (1) US11493884B2 (de)
EP (1) EP3599517B1 (de)
JP (1) JP7063949B2 (de)
CN (1) CN112286031B (de)
RU (1) RU2742378C1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3599516B1 (de) * 2018-07-24 2024-04-03 Harry Winston SA Retrogrades tourbillon oder karussell eines uhrwerks
EP4266131A1 (de) * 2022-04-22 2023-10-25 Blancpain SA Dreidimensionales karussell für uhrwerk
EP4276545B1 (de) 2022-05-13 2024-12-18 Blancpain SA Anterograder anzeigemechanismus für uhr

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EP1465024A1 (de) * 2003-04-03 2004-10-06 Franck Müller Watchland SA Zweiachsiges Tourbillon für Uhren, insbesondere Armbanduhren
CH705938A1 (fr) * 2011-12-23 2013-06-28 Manuf Et Fabrique De Montres Et Chronometres Ulysse Nardin Le Locle S A Rouage planétaire pour une pièce d'horlogerie.
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CH709331A2 (fr) 2014-03-11 2015-09-15 Seiko Instr Inc Mécanisme d'affichage, mouvement et pièce d'horlogerie.

Also Published As

Publication number Publication date
CN112286031A (zh) 2021-01-29
RU2742378C1 (ru) 2021-02-05
US11493884B2 (en) 2022-11-08
CN112286031B (zh) 2022-03-29
JP7063949B2 (ja) 2022-05-09
JP2021018250A (ja) 2021-02-15
EP3599517B1 (de) 2021-03-10
US20210026304A1 (en) 2021-01-28

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