EP3851919A1 - Repositionierungsvorrichtung für uhrwerk - Google Patents

Repositionierungsvorrichtung für uhrwerk Download PDF

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Publication number: EP3851919A1
Authority: EP; European Patent Office
Prior art keywords: return spring; repositioning; hammer; elastic arm; repositioning device
Prior art date: 2020-01-20
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

EP20152713.2A

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English (en)

French (fr)

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EP3851919B1 (de

Inventor

Anthony Krüttli

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Patek Philippe SA Geneve

Original Assignee

Patek Philippe SA Geneve

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2020-01-20

Filing date

2020-01-20

Publication date

2021-07-21

2020-01-20 Application filed by Patek Philippe SA Geneve filed Critical Patek Philippe SA Geneve

2020-01-20 Priority to EP20152713.2A priority Critical patent/EP3851919B1/de

2021-07-21 Publication of EP3851919A1 publication Critical patent/EP3851919A1/de

2024-05-01 Application granted granted Critical

2024-05-01 Publication of EP3851919B1 publication Critical patent/EP3851919B1/de

Status Active legal-status Critical Current

2040-01-20 Anticipated expiration legal-status Critical

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Classifications

- 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
- G04F7/0804—Watches or clocks with stop devices, e.g. chronograph with reset mechanisms
- 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
- G04F7/0842—Watches or clocks with stop devices, e.g. chronograph with start-stop control mechanisms
- G04F7/0847—Watches or clocks with stop devices, e.g. chronograph with start-stop control mechanisms with column wheel
- 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
- G04F7/0842—Watches or clocks with stop devices, e.g. chronograph with start-stop control mechanisms
- G04F7/0857—Watches or clocks with stop devices, e.g. chronograph with start-stop control mechanisms with single push-button or actuation member for start-stop and reset

Definitions

the present invention relates to a repositioning device for a horological mechanism, that is to say a device designed to place and return an organ to a predetermined position.
the repositioning device is a device for resetting a hand, such as a chronograph hand, a chronograph counter hand, a second or a fraction of a second hand.
the present invention relates to a repositioning device for watchmaking comprising a repositioning cam, a hammer, a return spring and a control device.
the control device is arranged to retain the hammer in a rest position against the action of the return spring, release the hammer so that it strikes the repositioning cam under the action of the return spring and makes it rotate until in locking it in a predetermined position, and returning the hammer to its rest position against the action of the return spring.
the control device is typically operable by the user by means of one or more push buttons.
Such a repositioning device is described for example in the book “Theory of horology” by Charles-André Reymondin et al., October 1998, in chapter 11 .
the figure 7 represents the graph G of the moment of force applied by the return spring to the hammer as a function of the angular position of the hammer, the position P0 being the position of the hammer locking the repositioning cam, the position P1 being the rest position of the remote hammer of the repositioning cam.
the slope of this graph G is the stiffness of the spring.
This force can be reduced by reducing the stiffness of the return spring as illustrated by graph G ', but then the force of the return spring is also reduced, which risks no longer being sufficient to reposition the cam.
a minimum force is generally chosen for repositioning the cam in order to avoid sudden movements that generate wear or cause malfunctions of the mechanism such as the detachment or deformation of the needle for example. If the force which actuates the control device does not come from the user but from a mainspring, for example in the case of an automatically actuable control device, the high moment of force to be overcome for the return of the hammer in its rest position results in high energy consumption in the mechanism.
the present invention aims to reduce the moment of force to be overcome by the control device for the return of the hammer to its rest position without harming the repositioning function of the cam.
the invention further provides a timepiece, such as a wristwatch or a pocket watch, comprising this repositioning device.
stiffness is understood to mean tangential stiffness.
the repositioning device 1 for a timepiece according to a particular embodiment of the invention, mounted on a frame 2.
the repositioning device 1 comprises a control member 3, a hammer 4 pivoted at a point 5, a return spring 6 acting on the hammer 4 and a repositioning cam 7 pivoted at a point 8.
the control member 3 is here a column wheel comprising a ratchet 9 and columns 10, but it could be of a other type, for example a cam shuttle.
the hammer 4 comprises a nose 11 arranged to cooperate with the control member 3 and a actuating surface 12 arranged to cooperate with the repositioning cam 7.
the repositioning cam 7, typically a heart, is secured to a member (not shown) that it is desired to be able to return to a predetermined position, corresponding for example at the zero of a graduation.
the member can thus be an indicator member such as a chronograph hand, a chronograph counter, a second or a fraction of a second hand.
the repositioning device 1 is part of the chronograph mechanism and the control member 3 also serves to control the chronograph clutch and / or a chronograph brake.
the member integral with the repositioning cam 7 is an element of an animation that the timepiece includes.
the return spring 6 maintains the nose 11 of the hammer 4 resting against a column 10 of the control member 3. In this position of the hammer 4, called the rest position, the actuating surface 12 is out of contact with the repositioning cam 7.
the nose 11 of the hammer 4 falls into a void between two columns 10 and the actuating surface 12 strikes the repositioning cam 7 under the 'action of the return spring 6.
the support of the actuating surface 12 on the repositioning cam 7 rotates the latter until the actuating surface 12 comes to rest against two shoulders 13 of the repositioning cam 7 to exert a force directed towards the center of the cam 7, which stops both the hammer 4 and the repositioning cam 7.
the driving force for each movement of the control member 3 is supplied by the user, for example via a pusher acting on a rocker of control acting on the ratchet 9 via a control hook. Depending on the intended application, one could nevertheless provide for automatic actuation of the control member 3 by a mainspring.
the hammer 4 In the case of a chronograph mechanism, the hammer 4 is returned to its rest position by a column 10 of the control member 3 when the start of the chronograph is triggered. If the chronograph is three-stroke, that is to say has only one push-button to successively control the start, stop and resetting of the chronograph hand, the nozzle 11 of the hammer 4 is resting against a column 10 of the control member 3 during the operating and stopping phases of the chronograph.
the chronograph mechanism is two-stroke, that is to say comprises a first pusher to control the start and stop of the chronograph hand and a second pusher to control the reset
the nozzle 11 of the hammer 4 leans against a column 10 of the control member 3 during the operating phase but is opposite a vacuum between two columns 10 during the stopping phase, the hammer 4 then being retained in its position of rest by an auxiliary control member, such as a lock, controlled by the second pusher, as is known per se.
the return spring 6 is specially shaped to reduce the moment of force to be overcome in order to return the hammer 4 to its rest position while ensuring sufficient force for the repositioning of the repositioning cam 7 during the fall of the hammer 4.
the return spring 6 is in the form of an elastic arm or blade forming part of a part 14 further comprising a base 15 and a rotating element 16, the elastic arm 6 connecting the base 15 to the rotating element 16 , only the elastic arm 6 is deformed during the operation of the device 1.
the base 15 is fixed, for example by means of pins or screws, to the frame 2.
the rotary element 16 is fixed, for example by means of pins or screw, hammer 4 to turn around point 5 with hammer 4.
Part 14 is typically one-piece. It is for example made of metal, alloy, silicon, plastic, mineral glass or metallic glass. It can be produced by machining or by the LIGA technique, in particular in the case where it is made of a metal or alloy, by deep reactive ionic etching known as DRIE, in particular in the case where it is made in silicon, by molding, in particular in the case where it is made of plastic or metallic glass, or by laser cutting, in particular in the case where it is in mineral glass.
DRIE deep reactive ionic etching
the part 14 Due to the shape of its elastic arm 6, the part 14 has a preferred direction of rotation of its rotary element 16 around point 5 with respect to its base 15, this direction being defined as that which allows, from a rest state of the isolated part 14 in which its elastic arm 6 is at rest (without deformation), the greatest relative angular displacement of the rotary element 16 with respect to the base 15. This preferred direction of rotation is clockwise to the figure 1 .
⁇ be the angular position of the rotating element 16 of the isolated part 14 with respect to the base 15, ⁇ being equal to zero when the isolated part 14 is at rest, that is to say when its elastic arm 6 is at rest, and increasing with the relative angular displacement of the rotary element 16 with respect to the base 15 in the preferred direction of rotation of the isolated part 14;
the figure 2 illustrates the evolution M ( ⁇ ) of the elastic restoring moment exerted by the elastic arm 6 in the isolated part 14 as a function of the angular position ⁇ of the rotary element 16 around the point 5 with respect to the base 15.
the isolated part 14 having a curve M ( ⁇ ) of the type shown in figure 2 differs from classical elastic structures. Its properties are based on a sinuous shape of its elastic arm 6 which deforms so as to generate a substantially constant elastic restoring moment (the curve M ( ⁇ ) has a plateau between ⁇ 1 and ⁇ 2 ) over a predetermined range of angular positions of its element rotary 16 relative to its base 15. Obtaining such an elastic arm 6 requires a specific and parameterized design.
the topological optimization referred to in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic arm.
the geometric shape of the elastic arm 6 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the part 14 to be designed as well as a constraint “(M max -M min ) / ( (M max + M min ) / 2) ⁇ 0.05 ”.
the equation “(M max -M min ) / ((M max + M min ) / 2) ⁇ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range.
the elastic arm or rocker return spring 6 is designed, in particular by virtue of its shape, to exert, in the part 14, a substantially constant elastic return moment (constancy of 5%) over a range of angular positions of the rotary member 16 relative to the base 15 of at least 10 °, preferably at least 15 °, more preferably at least 20 °.
the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bézier curve of order 4 based on control points Q 3 to Q 6 .
the graph of the figure 3 shows the elastic arm 6 of the particular part 14 that the applicant has designed, the geometry of the arm 6 being defined by a curve passing through the set of coordinates of points defined in Table 2 above. This graph is produced in an orthonormal coordinate system.
the figure 4 represents the results of a simulation of the evolution of the elastic return moment of the particular part 14 thus produced as a function of the angular position ⁇ of its rotary element 16 with respect to its base 15.
the simulation carried out considers a part 14 made of silicon covered with a layer of silicon oxide, but any suitable material can be used.
materials such as metallic glasses (for example Vitreloy 1b), alloys such as Nivaflex® 45/18 (alloy based on cobalt, nickel and chromium), nickel-phosphorus or CK101 (structural steel non-alloy), or plastic are also suitable. It is important to take into account the relationship between the elastic limit and the Young's modulus of the material when choosing the material constituting the elastic arm 6.
the stiffness of the part 14, more precisely of its elastic arm 6, is the derivative of the function M ( ⁇ ) defined above.
the stiffness is zero at the angular positions ⁇ a and ⁇ b and negative between these positions ⁇ a and ⁇ b .
the part 14 is therefore arranged so that, on each displacement of the hammer 4 from its position where it locks the repositioning cam 7 in its rest position remote from the repositioning cam 7 against the action of the arm elastic or return spring 6, the rotary element 16 moves in a predetermined range of angular positions relative to the base 15, this range being included in the range of positions [ ⁇ 1 , ⁇ 2 ] associated with the part 14 and comprising at least part of the range of positions [ ⁇ a , ⁇ b ] in which the stiffness of the elastic arm 6 is zero or negative.
the stiffness is zero or negative in at least 20%, preferably at least 40%, preferably at least 60%, preferably at least 80% of the predetermined plate.
said predetermined range is included in the range [ ⁇ a , ⁇ b ] or constituted by the latter. More preferably, said predetermined range is included in the range] ⁇ a , ⁇ b [where the stiffness is negative at each point.
part 14 is pre-armed. More precisely, the base 15 is positioned when it is mounted on the frame 2 so that the return spring 6 is armed with ⁇ arm degrees when the actuating surface 12 bears against the shoulders 13 of the cam. repositioning 7, this value ⁇ arm being the lower limit of the above-mentioned predetermined range.
the length of the predetermined range is defined by the stroke of hammer 4. In the example illustrated, it is 15 °.
the moment of force to be overcome in order to bring the hammer 4 back into its rest position can be reduced compared to a traditional return spring, for the same force applied to the repositioning cam 7 when it is in its locked position.
the figure 5 shows different curves representative of a normalized moment of force M ( ⁇ ) exerted by the elastic arm 6 in the isolated part 14 for different variations of section of the elastic arm 6.
the highest curve, designated by C1 corresponds to an arm elastic 6 of constant section and thickness (width) 70 ⁇ m.
the curves located below the curve C1 correspond to an elastic arm 6 whose thickness increases linearly from the rotary element 16 to the base 15, the thickness at the point of junction with the base 15 being 70 ⁇ m for each curve, the thickness at the junction point with the rotating element 16 being 69 ⁇ m for the first curve C2 under curve C1, 68 ⁇ m for the second curve C3 under curve C1, 67 ⁇ m for the third curve C4 under the curve C1, and so on by decrementing 1 ⁇ m.
the stiffness decreases (the moment of force decreases more) in the range of winding angles of interest where the stiffness is negative when the variation of section is increased. It should also be noted that the length of the range of winding angles where the stiffness is negative increases.
the figure 6 shows various curves representative of a normalized moment of force M ( ⁇ ) exerted by the elastic arm 6 in the isolated part 14.
the uppermost curve, designated by C1 corresponds to an elastic arm 6 of constant section and of thickness 70 ⁇ m.
the curves located below the curve C1 correspond to an elastic arm 6 whose thickness increases linearly from the rotating element 16 to the middle of the elastic arm 6 and decreases linearly from the middle of the elastic arm 6 to the base 15, the thickness in the middle of the elastic arm 6 being 70 ⁇ m for each curve, the thickness at the junction point with the rotating element 16 and at the junction point with the base 15 being 69 ⁇ m for the first curve C2 'under the curve C1, 68 ⁇ m for the second curve C3 ′ under the curve C1, 67 ⁇ m for the third curve C4 ′ under the curve C1, and so on by decrementing by 1 ⁇ m.
the elastic arm 6 has a variable section
this typically varies in a strictly monotonic manner (it increases or decreases without interruption but not necessarily linearly) over at least one continuous portion of the elastic arm representing 10% , preferably 20%, preferably 30%, preferably 40%, of the length (curvilinear) of the elastic arm.
the variation of the section is also chosen to make the stiffness of the elastic arm 6 more negative over the range [ ⁇ a , ⁇ b ] or at least over the part of the predetermined range which intersects with the range [ ⁇ a , ⁇ b ], with respect to an elastic arm of the same shape as the arm 6 but of constant section.
the shape of the repositioning cam 7 can be adapted to the behavior of the return spring 6 so that the moment of force applied by the hammer 4 to the repositioning cam 7 is substantially constant during the movement of the latter. This avoids force peaks on the cam 7, generators of wear or causes of malfunction. If the stiffness of the return spring 6 is substantially zero in the working range, the shape of the cam 7 will therefore be chosen so that the lever arm is substantially constant. If the force of the return spring 6 varies within the working range, the shape of the cam 7 will be such that the variation of the lever arm with which the hammer 4 acts on the cam 7 compensates for the variation in the force of the return spring. 6.
the return spring or elastic arm 6 may have a shape different from that illustrated on figure 1 . It can in particular take a form as described in the article “Functional joint mechanisms with constant-torque outputs”, Mechanism and Machine Theory 62 (2013) 166-181, Chia-Wen Hou et al.
the return spring 6 could comprise several elastic arms connecting the base 15 to the rotary element 16, like the devices described in the two articles "Design of adjustable constant-force forceps for robot-assisted surgical manipulation” and “Functional joint mechanisms with constant-torque outputs” mentioned above.
a single elastic arm 6 is sufficient since it has no guiding function - the rotary element 16 is on the hammer 4 which is guided by its axis - but only fulfills an elastic return function. It will also be noted that making the return spring 6 in the form of a single elastic arm has the advantage of greater compactness.
the choice of the number of elastic arm (s), their length and their thickness determines the intensity of the force produced. It is also possible to adjust the inclination of the elastic arm or arms relative to the rotary element 16 (in the plane of the part 14) to modify the intensity of the force produced.
Another modification of the invention could consist in making the part 14, of which the return spring 6 is part, in one piece with the hammer 4.
the hammer 4 could include several actuating surfaces arranged to act on several respective repositioning cams.
each hammer 4 could carry a roller which would cooperate with the respective repositioning cam 7.

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EP20152713.2A 2020-01-20 2020-01-20 Repositionierungsvorrichtung für uhrwerk Active EP3851919B1 (de)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
EP20152713.2A EP3851919B1 (de)	2020-01-20	2020-01-20	Repositionierungsvorrichtung für uhrwerk

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Application Number	Priority Date	Filing Date	Title
EP20152713.2A EP3851919B1 (de)	2020-01-20	2020-01-20	Repositionierungsvorrichtung für uhrwerk

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EP3851919A1 true EP3851919A1 (de)	2021-07-21
EP3851919B1 EP3851919B1 (de)	2024-05-01

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP2073077A1 (de) *	2007-12-21	2009-06-24	Omega SA	Stoßsichere vorrichtung für ein antriebsorgan eines uhrwerks
CH713787A2 (fr) *	2017-05-03	2018-11-15	Patek Philippe Sa Geneve	Dispositif horloger à organe de positionnement.

2020
- 2020-01-20 EP EP20152713.2A patent/EP3851919B1/de active Active

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP2073077A1 (de) *	2007-12-21	2009-06-24	Omega SA	Stoßsichere vorrichtung für ein antriebsorgan eines uhrwerks
CH713787A2 (fr) *	2017-05-03	2018-11-15	Patek Philippe Sa Geneve	Dispositif horloger à organe de positionnement.

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
CHAO-CHIEH LAN ET AL.: "2011 IEEE International Conférence on Robotics and Automation", 9 May 2011, SHANGHAI INTERNATIONAL CONFÉRENCE CENTER, article "Design of adjustable constant-force forceps for robot-assisted surgical manipulation"
CHARLES-ANDRÉ REYMONDIN ET AL.: "Théorie d'horlogerie", October 1998
CHIA-WEN HOU: "Functional joint mechanisms with constant-torque outputs", MECHANISM AND MACHINE THEORY, vol. 62, 2013, pages 166 - 181, XP028970320, DOI: 10.1016/j.mechmachtheory.2012.12.002

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