EP3559757B1 - Uhrwerk für eine uhr - Google Patents

Uhrwerk für eine uhr

Info

Publication number
EP3559757B1
EP3559757B1 EP17835621.8A EP17835621A EP3559757B1 EP 3559757 B1 EP3559757 B1 EP 3559757B1 EP 17835621 A EP17835621 A EP 17835621A EP 3559757 B1 EP3559757 B1 EP 3559757B1
Authority
EP
European Patent Office
Prior art keywords
movement
control device
actuator
display
gear train
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
EP17835621.8A
Other languages
English (en)
French (fr)
Other versions
EP3559757A1 (de
Inventor
Stephen Forsey
Robert Greubel
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.)
GREUBEL FORSEY SA
Original Assignee
Greubel Forsey 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
Application filed by Greubel Forsey SA filed Critical Greubel Forsey SA
Publication of EP3559757A1 publication Critical patent/EP3559757A1/de
Application granted granted Critical
Publication of EP3559757B1 publication Critical patent/EP3559757B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • G04B27/00—Mechanical devices for setting the time indicating means
    • G04B27/001—Internal gear therefor, e.g. for setting the second hand or for setting several clockworks
    • 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
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses
    • 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
    • G04B19/02—Back-gearing arrangements between gear train and hands
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0823—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement
    • G04F7/0833—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement acting perpendicular to the plane of the movement
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0866—Special arrangements
    • G04F7/0895—Special arrangements with a separate barrel for the chronograph functions
    • 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
    • G04B1/12—Driving mechanisms with mainspring with several mainsprings
    • 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
    • G04B13/007—Gearwork with differential work

Definitions

  • the present invention relates to the field of watchmaking. More particularly, it concerns a movement for a timepiece.
  • Complicated watches typically require not only a large size but also significant torque to operate. To ensure an adequate power reserve, the mainspring barrels must therefore be large. Consequently, the greater the number of complications, the larger the watch, since current design techniques dictate that each complication be built to a conventional watchmaking scale.
  • the oscillations of the regulating organ can be disrupted. Indeed, if no complications consume energy, the regulating organ receives a high torque, which decreases as the complications become more active and their energy demands increase. Since the regulating organ's behavior varies according to the torque it receives, this behavior can be highly variable, thus compromising isochronism.
  • the aim of the present invention is therefore to at least partially overcome at least one of the aforementioned drawbacks, and thus to offer a watch movement with increased power reserve and improved isochronism.
  • the document EP0108412 describes a time-setting device comprising several knurled shafts with a diameter of 0.8 mm. These shafts are involved exclusively in setting the time of the movement and therefore cannot help overcome these drawbacks, since this device is not involved in the transmission of torque between the mainspring barrel and the regulating organ of the movement. Furthermore, the document EP 2 821 862 reveals a dead second mechanism in which relatively small gears are involved in controlling the corresponding display organ.
  • the invention relates to a movement for a timepiece, comprising at least one energy source, for example one or more barrels, a finishing gear train kinematically linking said energy source to a regulating organ such as an escapement associated with a balance wheel and hairspring, and a display organ arranged to be driven by said energy source according to the regulating organ.
  • a regulating organ such as an escapement associated with a balance wheel and hairspring
  • the movement further comprises an actuator arranged to influence, that is, to control, block, release, trigger, or vary the speed of the rotational transmission between the power source and the display unit, and a control device arranged to control the actuator.
  • the control device comprises entities that are either a set of at least two elements fixed together and rotating about a common axis, or a single element rotating about its own axis, all of these entities having a diameter less than or equal to 2.5 mm, and/or, in the case of a lever, the maximum radius measured from its pivot point being less than or equal to 1.25 mm.
  • the actuator is located within the finishing gear or is integrated into the power source.
  • control mechanism consists of a set of moving parts with extremely low inertia, and therefore requires significantly less torque to drive them. Consequently, the operation of the control mechanism requires less torque than usual from the power source and the finishing gear train, which reduces stress on the regulating organ and increases the movement's power reserve. Furthermore, the use of smaller components also allows for the development of complications with fewer components and greater simplicity.
  • the said actuator may be, for example, a differential gear, a cam, a clutch, a lever, a rake, a rack, or a combination of several of these elements.
  • said actuator is located in said finishing gear, and/or is integrated into said energy source, such as for example by being provided in or on the drum of a barrel.
  • said control device can be arranged to be controlled directly by said regulating organ.
  • the actuator can be located in an additional kinematic chain extending from the energy source, with the control device being controlled by the regulating element.
  • the torque used by the actuator can thus be independent of that distributed by the finishing gear, which further reduces the influence of the regulating element on its operation.
  • the power source may consist of a single drive unit, or alternatively, it may consist of a first drive unit arranged to drive the finishing gear train, and a second drive unit arranged to drive the additional kinematic chain.
  • This latter option minimizes the impact of the control device and actuator on the operation of the regulating organ, and also allows for optimization of the torque supplied to each part of the movement by selecting appropriate mainspring barrels.
  • control device can be arranged to be controlled by a user, for example in the case where the control device drives a chronograph or similar.
  • said control device can be arranged to be driven by said finishing gear.
  • control device and actuator are located within the finishing gear, the regulating member comprising an oscillator with a diameter of 5 mm or less.
  • control device which includes a set of reduced-sized moving parts, interfaces between a conventionally sized drive source and a reduced-sized oscillator.
  • said actuator may be driven by said energy source or by said finishing gear, and said control device is controlled directly or indirectly by said regulating member.
  • the movement may further include an additional display device arranged to be driven by said finishing gear or by said regulating organ.
  • This additional display organ may even be integrated into an escape wheel or into a tourbillon or carousel cage.
  • At least part of said finishing gear and/or at least one other kinematic linkage may exclusively be composed of entities being either a set of at least two elements joined together and rotating around a common axis, or a single element rotating around its own axis, said entities having a size less than or equal to 2.5mm.
  • the invention relates to a timepiece comprising a movement as defined above.
  • FIG 1 schematically illustrates a first variant of a watch movement 1 according to the invention.
  • This movement 1 comprises a power source 3 including at least one driving element, such as a or Several barrels, an electric motor or similar, and a finishing train 5a, 5b that links the power source 3 to a regulating organ 7 constituting a time base.
  • the regulating organ often also called a “regulator,” typically includes an escapement and a balance-spring oscillator, but also, for example, a tuning fork regulator, a tourbillon, or any other known form of regulator.
  • an actuator 9 is incorporated into the finishing train 5a, 5b and drives a display organ 11.
  • the finishing train 5a, 5b may be of conventional size ("watch size").
  • watch-sized mobiles commonly used in finishing trains have a diameter of up to around 12 mm. It is known that some wheels or pinions can have a very small diameter, down to around 0.90 mm, for example in the case of an escapement pinion, but these wheels or pinions are part of larger components, whose overall diameter (defined by the largest wheel composing the component) is significantly greater.
  • large component we mean either a set of at least two elements (wheel, pinion, cam, etc.) fixed together in rotation around a common axis, or a single rotating element (wheel, pinion, cam, etc.) around its own axis and which is not fixed in rotation to another element.
  • This actuator 9 is in turn controlled by a control device 13, which receives information from the regulating organ 7 via an arbitrary kinematic linkage 8.
  • the control device 13 comprises moving parts (wheels, cams, etc.) all of which are “reduced size,” that is, they have a diameter less than or equal to 2.5 mm, or even less than or equal to 2 mm, 1.5 mm, or even 1 mm, as well as any other components of a size suitable for interacting with such moving parts.
  • the kinematic linkage 8 may consist of moving parts of clockwork size, or of reduced size (that is, all having a diameter less than or equal to 2.5 mm, or even less than or equal to 2 mm, 1.5 mm, or even 1 mm), and the kinematic linkage 10 between the control device 13 and the actuator 9 may also be of reduced size as defined above.
  • control device occupies a significantly reduced space, which also allows for an increased number of complications controlled by the control device 13 (chronograph, date, other display, etc., see below) that can be integrated into a given volume, if necessary, without requiring substantial additional torque for their operation, and allowing for a simplification and/or reduction in the number of components for a given mechanism.
  • the control device 13 receives energy directly from the regulating organ, which is not normally possible without disrupting the latter. Therefore, a power take-off directly from the escapement wheel or even the balance wheel could be considered, given that the torque extracted is negligible compared to that of the conventional case.
  • the control device 13 is arranged to control the actuator 9 in order to distribute torque arriving from the drive unit 3 to the display 11.
  • the actuator 9 could be a differential gear, on which the control device 13 acts to distribute torque to the display 11, by braking, locking, or releasing an input or output, for example, to create a differential-type clutch without interrupting the kinematic linkage.
  • the actuator 9 could be a clutch, whose switching between the engaged and disengaged states is arranged to occur in response to a small control force.
  • Actuators 9 based on racks or pinions, one or more cams, or levers are also conceivable.
  • the actuator 9 to be a gearbox, by example consisting of an epicyclic gear train, the control device thus performing a change of speed of the display.
  • the display 11 may be a date display (Western or otherwise), a display of the month, year, week, days of the week, moon phase, tides, biological, astronomical, or astrological cycles, an hour and/or minute and/or second display, a lightning bolt, or any other time-related display.
  • the kinematic linkage 14 between the actuator 9 and the display element 11 may be of clockwork size or of reduced size as defined above. In the latter case, the display element may optionally be smaller than conventional and may be viewed through an optical device such as a magnifying glass.
  • the finishing gear train 5a, 5b consists of watch-sized components, and the power source provides conventionally sized torque
  • the display 11, as well as the additional displays 11a can also be conventionally sized.
  • the movement according to the invention thus allows a conventionally sized display to be controlled by means of a reduced-sized control device.
  • FIG 8 schematically illustrates an architecture that corresponds to the functional diagram of the figure 1
  • This construction has been represented very schematically and is in no way to scale.
  • some kinematic links have simply been represented by arrows, as those skilled in the art know how to implement them using conventional gears (for example), which also applies to the figures 9 to 14 .
  • the regulating organ 7 comprises a balance wheel and hairspring assembly 7a, which cooperates with an anchor 7b and an escape wheel 7c in a known manner.
  • the actuator 9 is a differential gear comprising an input 9a and two outputs 9b and 9c.
  • this differential is of the spherical type, with a first sun wheel serving as the input and arranged to be driven by a mainspring barrel 3 acting as the power source.
  • a second sun wheel serves as the first output 9b, which drives the regulating organ 7.
  • the second output 9c is a planet carrier, which carries a plurality of bevel gears 101 that mesh with each of the sun wheels 9a and 9b in a known manner.
  • the control device 13 includes a constant-radius cam 13a, part of a moving part with a maximum diameter of 2.5 mm, driven directly or indirectly by the escapement pinion 7d, such that it is continuously driven when the movement 1 is in operation.
  • This cam 13a is positioned within a first fork 13b of a double fork 13c, which is pivoted appropriately on a frame element.
  • a second fork 13d engages with an external toothed section 9d in the differential's planet carrier 9c.
  • This toothed section 9d may be conventional, edge-cut, double edge-cut, or any other suitable toothed section or arrangement with similar functionality.
  • the double-fork 13c oscillates between two extreme positions arranged to release the planet carrier 9c in steps, typically one tooth per alternation of the double-fork.
  • the double-fork 13c oscillates between two extreme positions arranged to release the planet carrier 9c in steps, typically one tooth per alternation of the double-fork.
  • the control device 13 controls the distribution of torque to the display 11, by blocking and releasing it successively.
  • the display 11 can be advanced in steps over a desired period.
  • the manufacturer can plan to advance the display 11 at a rate of one step per second, per minute, per hour, per day, or at any other desired rate, substantially without affecting the torque supplied to the regulating element 7. Isochronism can thus be improved.
  • this arrangement allows for a step-by-step display without requiring any spring to be wound, or a jumper to be overcome, as is typically the case in such conventional displays.
  • the torque requirement is thus reduced, thereby increasing the power reserve of movement 1.
  • FIG 2 illustrates a variant of a movement 1 according to the invention, which differs from that of the figure 1 in that the control device 13 is itself controlled by a user action, schematically represented by the dashed arrow 15.
  • the user can, for example, press a push button, a latch, or equivalent, or can rotate a ring or similar mechanism.
  • the torque that drives the control device 13 is thus supplied by the user, and therefore there is no power take-off on the regulating element or the finishing gear for the operation of the control device 13.
  • the actuator 9 can be a conventional or differential clutch enabling the operation of a counter such as a chronograph or countdown timer, a tachometer, or similar device.
  • the actuator 9 can be a gearbox, for example, composed of an epicyclic gear train, which allows the display element 11 to advance or retract (depending on the gear ratios) at one or more speeds higher than its normal operating speed, in order to perform a rapid correction of the display element 11, for example, when setting the time.
  • FIG 9 schematically illustrates an architecture that corresponds to the functional diagram of the figure 2 This construction has been represented very schematically, and is in no way to scale.
  • the actuator 9 is illustrated as an epicyclic gearbox 9f, which allows the display 11 to be driven at different speeds under the control of the control member 13, which includes one or more small moving parts (not illustrated) which are controlled by the pusher 13z.
  • This gearbox 9f takes its force on an axis 9e which comprises the finishing gear 5a, 5b, and can take on a suitable shape.
  • Another type of gearbox particularly suited to this role is a differential gear with a first input arranged to be driven by the barrel 3, a second input arranged to be locked or unlocked by the control member 13, and an output that drives the display 11.
  • the second input is equipped with a disengageable linkage, such as a ratchet, friction, or similar device, which serves to kinematically connect it to the first input when the second input is not locked.
  • the differential can be arranged so that its planet carrier acts as said second input.
  • the gear ratio between the first input and the output is consequently 1:1.
  • the planetary gears act as reversers, and the gear ratio between the first input and the output consequently becomes 1 to -1, or another negative ratio depending on the number of teeth chosen and the differential's architecture (spherical, flat, etc.).
  • This type of differential reverser is known, for example, from the document WO2017071887 and therefore belongs to the knowledge of a person skilled in the art.
  • Such an inverter allows, for example, to provide a countdown timer on demand (if, for example, the kinematic chain between the actuator and the display 11 also includes a clutch in order to constitute a chronograph), or to make small corrections via a push button if the movement is ahead.
  • the rotational speed of the output can be varied while maintaining the same sign for the gear ratio. In other words, the output will always rotate in the same direction.
  • the gear ratios can be chosen at will by a person skilled in the art.
  • the manufacturer can be given more choice regarding speed ratios, and even several different speeds if one, the other or even both second inputs of the two differentials are blocked.
  • gearboxes are suitable for clockwise display corrections controlled by a push button. For example, in the case of an 11-digit display showing minutes and hours, if the gear ratio is 1:1 when the second input(s) is/are free and 1:1440 when it/they are blocked, the display will complete a full 24-hour cycle in one minute.
  • gear ratios can be chosen at will, particularly in the case of a small gearbox (i.e., one with moving parts having a diameter of 2.5 mm or less).
  • FIG 3 illustrates yet another variant of a movement 1 according to the invention.
  • the actuator is not located within the finishing gear 5, but has its own kinematic linkage consisting of an additional gear 17 extending from the drive unit 3.
  • the drive unit can thus divide its torque between the finishing gear 5 and the additional gear 17 via a differential gear (not shown).
  • This differential can be arranged according to the design requirements to distribute the torque symmetrically between the two gears 5 and 17, or asymmetrically, depending on the gear ratios used. In this way, the torque supplied to each gear can be optimized for the operation of either the regulating element or the display. For example, a display requiring high torque and a regulating element requiring little energy, or vice versa, can be driven from a single barrel.
  • one of the gears 5, 17 can be driven from the drum of a barrel, the other from its shaft.
  • This variant has fewer components compared to the differential solution described above.
  • the diameters of the moving parts that serve as power take-offs on the drum and on the barrel shaft can be chosen accordingly.
  • the same comments regarding the size of the moving parts constituting the kinematic links 8, 10, and 14 also apply here.
  • the kinematic link 14 between the actuator 9 and the display element 11 would be of watch-like size.
  • the torque from the barrel 3 is divided by means of a differential gear 3c in a known manner.
  • the torque arriving at the input 3d of the differential 3c from the barrel 3 exits in two directions through each of the two outputs 3e (which leads to the regulating element 7) and 3f (which drives the display 11).
  • the shape of this differential is not significant and does not need to be described in further detail. Furthermore, the aspects that are identical to the variant of the figure 8 do not bear any reference signs and will not be described again.
  • the control device 13 is driven by the exhaust pinion 7d and is similar to that illustrated on the figure 8 Therefore, it does not need to be described a second time.
  • the actuator 9 has a toothed wheel 9g which interacts with the second fork 13d so as to be locked and released in steps at each alternation of the double-fork 13c.
  • This toothed wheel 9g is driven by the second output 3f of the differential, and is locked and unlocked in stages with each alternation of the double fork 13c.
  • the control device 13c thus controls the torque distribution between the barrel 3 and the display 11.
  • the variant of the figure 4 differs from that of the figure 3 in that the drive unit 3 comprises two separate energy sources 3a, 3b, such as a pair of barrels.
  • the torque used by the display 11 has no influence on the finishing gear 5, and cannot in any way disturb the regulating element 7.
  • the size of the two energy sources 3a, 3b can be chosen according to their respective roles. The same comments regarding the kinematic links 8, 10, and 14 also apply here.
  • FIG 11 illustrates a construction that corresponds to the diagram of the figure 4 , and will be described exclusively by its differences from that of the Figure 10 Again, this construction has been represented very schematically, and is in no way to scale.
  • the power source 3 comprises a first barrel 3a which drives the regulating organ, and a second barrel 3b which drives the display 11.
  • a distinctive feature of the construction illustrated here is that a toothed section on the barrel meshes directly with the escapement pinion 7d of the regulating organ, making the finishing train 5 as compact as possible and minimizing the number of components. This is made possible by the fact that the display 11 is not driven by the The finishing gear 5 is controlled by the latter. Indeed, the control device 13 only receives information from the regulating organ 7 (more specifically from the escapement pinion 7). The display drive is therefore entirely separate from the finishing gear, controlled by the control device 13, which regulates the rotation speed of the display based on the torque supplied by the second barrel 3b and thus sets the gear ratios for the display 11.
  • the escapement pinion 7d drives the control device 13, the toothed wheel being driven by the second barrel 3b, and driving the display device 11.
  • This variant allows the torque supplied by each of the barrels to be adapted according to its role, since the first barrel 3a can be adapted for driving the regulating organ 7, while the second barrel 3b can be more powerful in order to drive the display device 11.
  • the control device 13 again having moving parts with a diameter of 2.5mm at most, it consumes very little energy and therefore hardly disturbs the regulating organ 7. However, it can control higher torques from the second barrel 3b.
  • FIG. 5 illustrates a variant based on that of the figure 3
  • this version differs from the latter in that the control device 13 receives information from the finishing gear 5 upstream of the regulating member 7.
  • This variant allows the control device 13 to receive more torque, which in turn can supply more torque and/or force to the actuator 9 to activate/deactivate it. Consequently, the control device 13 can operate with an actuator 9 that requires more force to trigger its operation.
  • the same comments regarding the kinematic links 8, 10, and 14 also apply here.
  • figure 12 illustrates a construction that corresponds to the diagram of the figure 5 , and will be described exclusively by its differences from that of the figure 11
  • This construction has been represented very schematically, and is not to scale.
  • FIG. 6 illustrates yet another variant of a movement 1 according to the invention.
  • the actuator 9 is located directly in the finishing gear 5a, 5b, 5c
  • the control device 13 is also located in the same finishing gear 5a, 5b, 5c, upstream of the regulating member 7 and downstream of the actuator 9.
  • the control device 13 drives the actuator 9 by transmitting timing information to it from the regulating member 7.
  • the actuator can be, for example, a cam arranged in the finishing gear train 5a, 5b, or alternatively in a branch thereof, to advance the display element 11 in increments, and the regulating element 7 can itself be of reduced size.
  • the regulating element 7 can include a balance wheel with a diameter equal to or less than 5 mm, depending on the material chosen for its manufacture, and the control device 13 acts as an interface between the parts of the finishing gear train 5a, 5b which have a conventional horological size and the reduced-size regulating element 7.
  • the part of the finishing gear 5b which is located between the actuator 9 and the control device 13 can be composed of clock-sized or reduced-size mobiles, and the part 5c which links the control device 13 to the regulating organ is of course reduced in size in order to cooperate with the reduced-size regulating organ 7.
  • figure 13 illustrates a construction that corresponds to the diagram of the figure 6 This construction has been represented very schematically, and is in no way to scale.
  • the overall construction of the movement 1 is conventional, the barrel 3 being kinematically linked to the regulating organ 7 via a finishing gear 5.
  • a constant-radius cam 9j is mounted on one of the moving parts of the finishing gear, which is part of the actuator 9 and the control device 13. This cam interacts with a toothed wheel 103 via a hook 105 carried by a flexible arm 107.
  • the flexible arm 107 is attached to a rigid arm 109 extending from a fork 111 that cooperates with the cam 9j.
  • the rigid arm 109 oscillates about its pivot axis 113, advancing the toothed wheel 103 clockwise (in the figure) by one tooth increment.
  • the wheel 103 is positioned by a jumper 115 in a known manner.
  • the shape of the hook 105 and the flexibility of the arm 107 allow the hook 105 to skip teeth as it moves to the left. Since the wolf's toothed wheel 103 is kinematically linked to the display 11, the latter is also driven in turn.
  • FIG. 7 illustrates yet another variant of a movement 1 according to the invention.
  • the regulating member 7 is in direct kinematic connection with the driving member 3 via the finishing gear 5, and an additional display member 12 is provided downstream of the regulating member 7.
  • control device 13 takes information downstream of the regulating organ 7, or alternatively directly from the latter, and the actuator takes force from a moving part of the finishing gear 5 or alternatively directly from the energy source.
  • the actuator 9 can drive the display 11 under the control of the control device 13, and the regulating member 7 can drive an additional display member 12.
  • the kinematic linkage 8 between the regulating element 7 and the control device 13, as well as that between the latter and the actuator, will be of reduced size, and the one joining the finishing gear 5 to the actuator 9 can be of watch size or reduced.
  • the additional display element 12 could be located directly on the regulating element 7, for example by being integrated into an escape wheel, a tourbillon or carousel cage, or similar.
  • figure 14 illustrates a construction that corresponds to the diagram of the figure 7 This construction has been represented very schematically, and is in no way to scale.
  • the construction comprises a single barrel 3, whose torque is divided by a differential gear 3c in a known manner.
  • the torque arrives at a first sun wheel 3g and exits at a first output 3h (a second sun wheel) to drive the regulating organ 7, and at a second output 3i (a planet carrier) to drive the actuator 9.
  • first sun wheel 3g a second sun wheel
  • second output 3i a planet carrier
  • the actuator 9 shown here is a wheel carrying a single finger 9h, which is held by a retaining beak 13i which has a lever 13g.
  • the control device 13 consists of this lever 13g, which also provides the kinematic link 10 between the regulating member 7 and the actuator 9.
  • the lever 13g is actuated by a pin 8a carried by the rim of the balance wheel 7a, or by another element such as a plate that is rotationally fixed to the balance wheel 7a. It is therefore clear that the pin 8a constitutes the kinematic link 8 between the regulating organ 7 and the control device 13. It is also possible to actuate the lever 13g by the escapement pinion 7d or by an element driven by it.
  • Lever 13g pivots around a point at 1 o'clock, chosen here at one end of lever 13g to simplify the diagram. However, pivoting at an intermediate point, combined with a more realistic mechanism geometry, is preferable.
  • the "diameter" of the lever is twice its maximum radius measured from its pivot point 13h, and is at most 2.5 mm.
  • lever 13g and pin 8a are chosen so that, when balance wheel 7a oscillates, pin 8a strikes lever 13h and causes it to pivot. If the lever acts in the same plane as the balance wheel, this can be done without particular difficulty. If, however, the lever acts in a different plane, as implied by the figure 14 Beveled surfaces, cam surfaces or similar can be provided to ensure that the 13g lever is actuated in a suitable manner.
  • a spring return element 13j ensures that the lever 13g is brought back against the surface of the wheel 9 when it is not under the control of the pin 8a and can block the passage of the finger 9h. In doing so, with each oscillation of the balance wheel 7a, the actuator 9 completes one revolution, and drives the display 11 by one step.
  • lever 13g will be actuated once per oscillation of the balance wheel 7a. Furthermore, it is possible to provide several fingers (or a toothed section) on actuator 9 to select the desired gear ratio between the barrel and the display 11.
  • the additional display 12 is illustrated as being driven by the escapement pinion 7d included in the regulating organ 7.
  • the lever carries or actuates a hook which advances an additional actuator, for example of the type illustrated on the figure 13 , in order to trigger an additional display.
  • the actuator 9 and the control device 13 can be integrated into a single unit performing both functions, as is the case in the variant of the figure 13 Furthermore, the actuator 9 and/or the control device 13 can act as a kinematic link, as is notably the case with the figure 14 , and it is also possible that the actuator 9 is integrated into a drum of a barrel constituting the driving element 3.
  • Small-sized mobiles i.e. those forming part of the control device 13, as well as certain kinematic chains as mentioned above, can be manufactured for example by micromachining processes capable of defining elements with voxels on the order of a few hundred nanometers, and thus of creating shapes with a precision on the order of the micrometer.
  • Examples include LIGA processes, masking and engraving processes using a material slab, photostructuring of glass or quartz with a femtosecond laser, and high-resolution additive manufacturing in metal, epoxy, or ceramics.
  • Additional manufacturing is the general term for all manufacturing processes that involve adding material, particularly 3D printing, including 3D photolithography, laser sintering, and others. A more detailed discussion of this topic can be found in the Swiss patent application. CH360/16 .

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Measurement Of Unknown Time Intervals (AREA)

Claims (14)

  1. Uhrwerk (1) für eine Uhr, umfassend:
    - mindestens eine Energiequelle (3, 3a, 3b);
    - ein Finissage-Räderwerk (5, 5a, 5b, 5c), das die Energiequelle (3, 3a, 3b) kinematisch mit einem Regulierorgan (7) verbindet;
    - ein Anzeigeelement (11), das so ausgelegt ist, dass es von der Energiequelle angetrieben wird;
    - einen Aktuator (9), der so ausgelegt ist, dass er die Drehübertragung zwischen der Energiequelle (3, 3a, 3b) und dem Anzeigeelement (11) beeinflusst; und
    - eine Steuervorrichtung (13), die so ausgelegt ist, dass sie den Aktuator (9) steuert,
    dadurch gekennzeichnet, dass die Steuervorrichtung (13) Elemente umfasst, die aus folgenden ausgewählt sind:
    - eine Anordnung von mindestens zwei Elementen, die um eine gemeinsame Achse drehfest miteinander verbunden sind;
    - einem einzigen Element, das um seine eigene Achse drehbar ist,
    wobei die Elemente alle einen Durchmesser von weniger als oder gleich 2,5 mm aufweisen und/oder im Falle eines Hebels der maximale Radius, gemessen von seinem Drehpunkt, weniger als oder gleich 1,25 mm ist,
    und dass sich der genannte Aktuator (9) in dem genannten Finissage-Räderwerk (5, 5a, 5b) befindet oder in die genannte Energiequelle (3, 3a, 3b) integriert ist.
  2. Uhrwerk (1) gemäß Anspruch 1, wobei der Aktuator (9) mindestens eines der folgenden Elemente umfasst: ein Differentialgetriebe, einen Nocken, eine Kupplung, einen Hebel, einen Rechen, eine Zahnstange.
  3. Uhrwerk (1) gemäß einem der vorstehenden Ansprüche, wobei die Steuervorrichtung (13) so ausgelegt ist, dass sie von dem Regulierorgan (7) gesteuert wird.
  4. Uhrwerk (1) nach einem der vorstehenden Ansprüche, wobei sich der Aktuator (9) in einer zusätzlichen kinematischen Kette (17) befindet, die sich von der Energiequelle (3, 3a, 3b) aus erstreckt, wobei die Steuervorrichtung (13) durch das Regulierorgan (7) gesteuert wird.
  5. Uhrwerk (1) gemäß Anspruch 4, wobei die Energiequelle (3) ein einziges Antriebselement (3) umfasst.
  6. Uhrwerk (1) gemäß Anspruch 4, wobei die Energiequelle (3, 3a, 3b) ein erstes Antriebselement (3a) umfasst, das zum Antreiben des Finissage-Räderwerks (5) ausgelegt ist, sowie ein zweites Antriebselement (3b), das zum Antreiben der zusätzlichen kinematischen Kette (17) ausgelegt ist.
  7. Uhrwerk (1) gemäß einem der Ansprüche 1 bis 3, wobei die Steuervorrichtung (13) so ausgelegt ist, dass sie von einem Benutzer gesteuert werden kann.
  8. Uhrwerk (1) gemäß einem der Ansprüche 1 bis 3, wobei die Steuervorrichtung (13) so ausgelegt ist, dass sie durch das Finissage-Räderwerk (5, 5a, 5b) angetrieben wird.
  9. Uhrwerk (1) nach Anspruch 8, wobei sich die Steuervorrichtung (13) und der Aktuator (9) im Finissage-Räderwerk (5a, 5b, 5c) befinden und das Regulierorgan (7) einen Oszillator mit einem Durchmesser von 5 mm oder weniger umfasst.
  10. Uhrwerk (1) gemäß den Ansprüchen 4 und 8.
  11. Uhrwerk (1) gemäß einem der Ansprüche 1 bis 3, wobei der Aktuator (9) von der Energiequelle (3, 3a, 3b) oder vom Finissage-Räderwerk (5, 5a, 5b) angetrieben wird und die Steuervorrichtung (13) direkt oder indirekt von dem Regulierorgan (7) direkt oder indirekt gesteuert wird.
  12. Uhrwerk (1) gemäß einem der vorstehenden Ansprüche, die zusätzlich eine zusätzliche Anzeigeeinrichtung (11a, 12) umfasst, die so angeordnet ist, dass sie von dem Finissage-Räderwerk (5, 5a, 5b) oder von dem Regulierorgan (7) angetrieben wird.
  13. Uhrwerk (1) nach einem der vorstehenden Ansprüche, wobei mindestens ein Teil des Finissage-Räderwerk (5, 5a, 5b) und/oder mindestens eine weitere kinematische Verbindung (8, 10, 14, 17), die das Uhrwerk (1) umfasst, ausschließlich Elemente umfasst, die aus folgenden ausgewählt sind:
    - einer Anordnung von mindestens zwei Elementen, die um eine gemeinsame Achse drehfest miteinander verbunden sind;
    - einem einzigen Element, das um seine eigene Achse drehbar ist,
    wobei die Elemente einen Durchmesser von weniger als 2,5 mm aufweisen und/oder im Falle eines Hebels der maximale Radius, gemessen von seinem Drehpunkt, kleiner oder gleich 1,25 mm ist.
  14. Uhr mit einem Uhrwerk (1) gemäß einem der vorstehenden Ansprüche.
EP17835621.8A 2016-12-22 2017-12-14 Uhrwerk für eine uhr Active EP3559757B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH17132016 2016-12-22
PCT/EP2017/082873 WO2018114613A1 (fr) 2016-12-22 2017-12-14 Mouvement pour piece d'horlogerie

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CH721746A1 (fr) * 2024-04-19 2025-10-31 Concepto Holding Sa Système pour contrôler la vitesse et/ou le sens de déplacement d'un mécanisme pour mouvement de montre

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EP3559757A1 (de) 2019-10-30
CH713326A2 (fr) 2018-06-29
CH713326B1 (fr) 2022-04-29
WO2018114613A1 (fr) 2018-06-28

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