EP4462193B1 - Mechanisches uhrwerk, das ein bewegliches element umfasst, das ein anzeigeelement mit einer bremsvorrichtung umfasst - Google Patents

Mechanisches uhrwerk, das ein bewegliches element umfasst, das ein anzeigeelement mit einer bremsvorrichtung umfasst

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Publication number
EP4462193B1
EP4462193B1 EP24163635.6A EP24163635A EP4462193B1 EP 4462193 B1 EP4462193 B1 EP 4462193B1 EP 24163635 A EP24163635 A EP 24163635A EP 4462193 B1 EP4462193 B1 EP 4462193B1
Authority
EP
European Patent Office
Prior art keywords
spring
intermediate part
braking
braking spring
mechanical
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
EP24163635.6A
Other languages
English (en)
French (fr)
Other versions
EP4462193A1 (de
Inventor
Baptist Wyssbrod
David Philippon
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.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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Publication date
Application filed by ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Publication of EP4462193A1 publication Critical patent/EP4462193A1/de
Application granted granted Critical
Publication of EP4462193B1 publication Critical patent/EP4462193B1/de
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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
    • G04B35/00—Adjusting the gear train, e.g. the backlash of the arbors, depth of meshing of the gears
    • 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
    • G04B29/00—Frameworks
    • G04B29/02—Plates; Bridges; Cocks
    • 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
    • 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
    • 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
    • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/247—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator disc-shaped
    • G04B19/25—Devices for setting the date indicators manually
    • 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
    • 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
    • G04B1/16—Barrels; Arbors; Barrel axles

Definitions

  • the present invention relates to a mechanical watch movement comprising a moving part carrying a display element, in particular a hand, and equipped with an anti-shake device, also called an anti-shake device, formed by a braking device acting on the moving part to prevent shaking of the display element in rotation and also fluttering of this element when stopped, if necessary.
  • an anti-shake device also called an anti-shake device
  • the document CH 580301 discloses an anti-shake device for a horological movement, specifically a chronograph movement, hereafter also referred to as a 'chronograph movement', comprising a shaft fitted with a pinion, which meshes with a clutch wheel, referred to herein as a drive wheel, forming a clutch mechanism for a chronograph.
  • a shaft fitted with pivots to guide its rotation is also called an 'axis' in horology.
  • the anti-shake device for the chronograph seconds hand consists of a friction device comprising a wire spring bearing obliquely against the shaft, which has a frustoconical shoulder for this purpose.
  • the wire spring has a pivot point in the angle formed by this shoulder and a circular cylindrical portion, the diameter of which corresponds to the minimum diameter of the shoulder.
  • This cylindrical portion exerts an oblique force on the shaft at this point, causing the pinion teeth to press against the driving wheel and a lower annular surface of the shaft, opposite the shoulder and perpendicular to the axis defined by the shaft, to press axially against a bearing in which the chronograph wheel pivots.
  • the spring is designed to be straight when under no stress. spring is fixed to the movement frame on the side of one end while part of the side of the second end is under tension and presses against the shaft, as explained above.
  • This anti-shake device presents several problems in controlling the frictional force applied to the chronograph movement. Furthermore, there is no way to adjust this frictional force. Additionally, when the chronograph hand is retracted, the mainspring is subjected to an axial force that can damage it.
  • the wire or leaf spring is attached at its first end by riveting to a plate held in suspension by a rivet with a slotted head, similar to a screw, positioned on one side of a bridge opposite the side where the plate is located.
  • the rivet has an intermediate cylindrical section that is inserted into a hole in the bridge with a friction fit. This allows the rivet, and consequently the plate and the first end of the spring, to be rotated using a tool.
  • the second end of the friction spring is free and radially supported against a plastic washer press-fitted onto the seconds hand's arbor. This washer has a lateral groove into which the second end of the spring is placed.
  • the proposed system is very difficult to integrate into the watch movement.
  • the friction spring must be attached to the plate by inserting its first end into a slot and then pushing material along both sides of the slot to create an initial rivet.
  • the plate with the friction spring must be brought to one inside side of the bridge after inserting the rivet into the hole in the bridge from the other side.
  • the end of the rivet must be flattened and a second rivet made to secure the plate to the rivet. It can be seen that at each stage of the assembly of the The friction spring is attached to the plate and then to the bridge via two successive rivets, creating a high risk of damage.
  • the bridge, plate, and friction spring assembly is mounted in the watch movement, ideally simultaneously with the insertion of a pivot for the seconds hand arbor, which carries the grooved washer, into a bearing within the bridge.
  • This assembly requires that the spring not be superimposed on the grooved washer, as the spring is integral with the bridge, while the grooved washer, designed to receive the free end of the tensioned spring, is integral with the arbor. Therefore, there is a first mounting/dismounting position for the spring and a second working position in which the free end of the spring is brought into the groove of the washer, thus applying tension to the spring.
  • the watchmaker To switch between positions, the watchmaker must manipulate the rivet head with a tool, which releases the spring's tension, which is set during disassembly for maintenance. Thus, each time the second-stage moving part is assembled, the braking force must be readjusted.
  • the assembly method described here is difficult to implement and very time-consuming.
  • this anti-shake device only partially solves the problem of adjusting the torque applied to the seconds hand to prevent shaking, because the friction force is defined in particular by the profile of the lateral groove in the plastic washer and the shape of the end of the spring that is inserted into this groove and presses radially against the washer.
  • Such a friction force is difficult to control and reproduce, as it depends heavily on the dimensions of the spring and the groove, their respective configurations, and their respective surface finishes.
  • Another problem arises from the fact that assembling an intermediate part on the seconds hand's shaft will generate an increase in the radial beat of the hand, and therefore a greater variation than in the absence of such an intermediate part, especially if the spring pressed directly against a conventional shaft with less radial beat.
  • the present invention aims to solve the problems of the prior art mentioned above and also to propose an anti-shake device for a display mobile, arranged outside the gear train of the barrel to the escapement mobile, which is easy to mount and which can, in a preferred embodiment, be mounted in a preliminary step to the mounting of the mobile in question.
  • the present invention relates to a mechanical watch movement comprising a mainspring barrel, an escapement wheel associated with a mechanical resonator, a display wheel comprising a shaft for carrying a display element, and a braking device associated with the display wheel and comprising a braking spring and an intermediate piece arranged between the braking spring and the shaft of the display wheel.
  • This display wheel can be driven in rotation by the mainspring barrel but is not part of a gear train from the mainspring barrel to the escapement wheel.
  • the braking spring is arranged so as to generate a braking torque on the display wheel as soon as the latter is subjected to a rotational driving torque, via the intermediate piece against which this braking spring presses.
  • the intermediate piece and the braking spring are arranged so that the intermediate piece remains stationary and non-rotating during normal operation.
  • the intermediate piece has a lateral surface, pressing against a surface of revolution of said shaft, and a bearing surface against which the braking spring exerts an overall pressure force in the direction of the shaft to generate a friction force between the lateral surface and the surface of revolution which generates said braking torque.
  • the intermediate piece and the braking spring are configured so that said pressure force remains constant once the display mobile is mounted in the movement and the braking device is fully mounted and adjusted.
  • the intermediate piece exerts exclusively radial pressure on the shaft of the display mobile.
  • the braking spring is a wire spring or a leaf spring whose longitudinal axis is located in a geometric plane parallel to a general plane of motion.
  • the movement includes an eccentric whose axis of rotation is perpendicular to said geometric plane and which is arranged to press radially against the braking spring in order to be able to vary, by a rotation around its axis of rotation, said overall radial pressure force exerted by the braking spring on the intermediate part.
  • the mechanical watch movement 2 comprises a braking device 6 acting on the display wheel and comprising the braking spring 10 and an intermediate piece 8 arranged between the braking spring and a shaft 36 of the display wheel 30.
  • the braking spring is arranged so as to generate a braking torque on the display wheel as soon as this display wheel is subjected to a rotational driving torque, via the intermediate piece against which this braking spring presses.
  • the intermediate piece has a lateral surface 9, pressing against a surface of revolution 35 of the shaft, and a bearing surface 25 against which the braking spring exerts an overall pressure force in the direction of the shaft to generate a friction force between the lateral surface and the surface of revolution, this friction force generating the braking torque.
  • the braking torque is exerted on the first wheel/display wheel by the braking spring via the intermediate piece against which the braking spring presses.
  • the intermediate piece 8 and the brake spring 10 are arranged so that the intermediate piece remains stationary and without rotation in Normal operation.
  • the shaft 36 of the first moving part and the intermediate piece are configured so that the surface of revolution 35 of the shaft can slide on the lateral surface 9, experiencing a dynamic friction force that generates the braking torque. Before the sliding of the surface of revolution on the lateral surface, a static friction force generates the braking torque and thus holds the shaft stationary.
  • the intermediate piece 8 exerts an exclusively radial pressure on the shaft 36 of the first moving part 30.
  • the brake spring 10 exerts an overall exclusively radial pressure force on the intermediate piece.
  • the bearing surface 25 is opposite the lateral surface 9, meaning that the bearing surface is located on one side of the intermediate part 8, which is opposite another side of this intermediate part defining the lateral surface 9.
  • This variant is advantageous because the braking device bears on a machined part whose radial runout varies little, thus providing a constant braking torque for a given friction force between the surface of revolution 35 and the lateral surface 9.
  • the surface of revolution 35 of the shaft 36 is cylindrical and axial
  • the lateral surface 9 of the intermediate part is axial; that is, the cylindrical surface of revolution 35 and the lateral surface 9 are oriented along the axis of rotation 42 of the first moving part 30, which coincides with the central axis of the shaft 36, the lateral surface 9 and the cylindrical surface of revolution 35 therefore being parallel to this axis of rotation 42.
  • the intermediate part 8 and the braking spring 10 are configured so that said pressure force remains constant once the display mobile is mounted in the movement and the braking device is fully mounted and adjusted.
  • the brake spring 10 is a wire spring or a leaf spring whose longitudinal axis is located in a plane geometric parallel to a general plane 50 of the mechanical watch movement 2.
  • the intermediate piece 8 is a washer having a central cylindrical opening in which, without the interaction of the braking spring 10, the shaft 36 of the first moving part 30 would slide and rotate freely, said lateral surface 9 of this washer 8 being defined by the cylindrical surface, preferably circular (i.e. of revolution), of its central cylindrical opening.
  • the washer 8 has a circular groove 24 around its circumference defining the bearing surface 25 and into which at least part of the brake spring 10 is inserted, which exerts the radial pressure force.
  • the groove 24 has a V-shaped cross-section and the brake spring 10 is a wire spring with a circular cross-section, as shown in the figures. Figures 3 And 5 This arrangement allows the brake spring to be axially positioned in its central part in contact with the washer. The spring is therefore not free to move axially.
  • At least the portion of the washer 8 defining its central cylindrical opening is made of a copper-beryllium (CuBe) alloy when at least the portion of the shaft defining the surface of revolution 35 is made of steel, or vice versa.
  • CuBe copper-beryllium
  • This first variant provides good tribological results.
  • at least the portion of the washer defining its central cylindrical opening is made of polymers.
  • the entire washer is made of polymers.
  • the shaft is made of steel or a copper alloy (for example, CuBe or brass)
  • at least the portion of the washer defining its central cylindrical opening is made of bronze, nickel, or gold, particularly in the form of a A thin layer deposited on a base of another material, in the case of nickel or gold, or more generally a metallic alloy containing gold or nickel.
  • at least the part of the disc defining its central cylindrical opening is made of ceramic, notably ruby or zirconia.
  • the material of the braking spring can be selected to optimize its elastic characteristics and manufacturing process, without having to worry about friction and wear issues, since the washer, and more generally the intermediate component, is designed to be static—that is, stationary and non-rotating—during normal operation of the mechanical watch movement.
  • the washer to prevent its rotation, one can either modify the shape of the intermediate component and/or the shape of the braking spring, as will be explained in more detail later, or, particularly in the case of a washer, modify the materials forming the spring and at least the outer part of the intermediate component in contact with the spring, and/or apply a surface treatment to these components to ensure high friction between the braking spring and the intermediate component.
  • the braking spring 10 is arranged in the mechanical watch movement 2 such that a mid-section between its two end sections presses radially against the bearing surface 25 of the intermediate piece/washer 8. More precisely, the braking spring 10 is arranged so that a mid-section of this braking spring exerts said pressure force on the bearing surface 25 of the intermediate piece/washer 8. To this end, the two end sections of the braking spring, located respectively on either side of said mid-section, are constrained by two distant parts 16 and 20 of the watch movement so that this mid-section exerts the pressure force on the bearing surface of the intermediate piece/washer.
  • This configuration of the braking device is advantageous because it allows a Constant pressure of the brake spring on the bearing surface of the intermediate piece/washer. Furthermore, this configuration is less sensitive to vibration and shock than if the brake spring had an anchor point at one end and a contact point at the other.
  • the brake spring 10 is curved in its midsection, and the bearing surface 25 of the intermediate piece/washer 8 has a convex curvature in said geometric plane, relative to the shaft 36 of the first moving part 30, and specifically a circular curvature in the case of the washer, which the midsection of the brake spring follows along the bearing surface in a first embodiment.
  • the radius of curvature of the midsection is smaller than the average radius of curvature of the bearing surface, so that the brake spring presses on the intermediate piece/washer at two points on the bearing surface, i.e., at two distinct locations.
  • a spring with a circular cross-section presses locally at a pair of axially aligned points.
  • the latter exerts pressure at two pairs of angularly separated points, with each pair of points aligned along an axial direction. Therefore, it exerts pressure at "two points” in projection onto the general plane of the spring, which is parallel to the general plane of motion.
  • these variants do not preclude other advantageous variants in which the average radius of curvature of the central portion is provided to be larger than the radius of curvature of the bearing surface. Consequently, the radial pressure is then exerted at "one point” (i.e., at a pair of points aligned along an axial direction, but at a single point in projection onto the general plane of the spring / general plane of motion).
  • the braking spring 10 is not fixed to the movement by a specific part, but is kept under tension by two parts 16 and 20 of this
  • the movement against which two end portions of the brake spring, located respectively on either side of a central portion of this brake spring, are pressed is radially supported against the intermediate part, which is in particular the washer 8.
  • the direction of the force applied by the two parts 16 and 20 on the spring is reversed with respect to the direction of the reaction force of the intermediate part/washer 8 on the central portion of the spring.
  • FIG. 6 The variant of the Figure 6 is characterized by a braking spring 10A with a central portion having two bends 71 and 72 separated by a straight section 70 (unconstrained), which bears, substantially at its midpoint, against the circular washer 8. This ensures that the braking spring 10A bears at a single point on the washer 8 at all times.
  • Variants of Figures 7A to 7B are characterized by an intermediate piece 68 which is not circular, but is formed by a truncated washer with a straight area 80.
  • the braking spring 10 has, in its part median, an elbow 74 which is located opposite the right zone 80 of the truncated puck 68.
  • the spring 11 is straight/rectilinear without constraint and, when energized to press against the intermediate piece, it curves slightly (concave curvature as seen from the intermediate piece) so that it presses at both ends of the straight area 80 of this intermediate piece.
  • the braking spring 10, respectively 11 exerts two forces F1 and F2 at the two ends of the straight section 80, respectively.
  • the two forces F1 and F2 are globally radial, meaning that their sum at a midpoint is radial.
  • each of the two forces exerts a torque on the intermediate piece 68, so that if the spring moves longitudinally and one of the two forces F1 and F2 decreases relative to the other, the intermediate piece 68 automatically undergoes a small rotation to restore equilibrium between the two opposing torques acting on it.
  • the variant of the Figure 7B is preferable because the risk of rotation of the truncated washer is lower. Furthermore, this variant allows the desired braking torque to be maintained even if the brake spring undergoes some longitudinal displacement during a shock or sudden acceleration. However, the variant of the Figure 7A With a bent spring, it is less likely to undergo longitudinal displacement in the event of an impact.
  • the variant with a truncated washer is advantageous in preventing the intermediate part from rotating during normal operation, which is important for ensuring a constant braking torque as set.
  • the variants of Figures 7A and 7B ensure at all times a support at "two points" projected into the geometric plane of the spring.
  • a particular variant is schematically represented at the Figure 8
  • This variant like that of the Figure 6 is designed to ensure constant pressure of the brake spring 10B at a single point on the intermediate piece 78, which has a generally square shape with rounded corners.
  • the brake spring 10B has a bend 76 such that the two straight sections of this spring on either side of the bend have a The angle is greater than 90° but relatively close to this value, for example, an angle of 110°.
  • One of the rounded corners of the intermediate piece is positioned within the bend 76 of the spring, which, when this spring and the intermediate piece 78 are stationary, exerts a substantially radial force F on the intermediate piece.
  • the braking device 6 comprises an eccentric 20 whose axis of rotation is perpendicular to the general plane 50, and therefore parallel to the central axis of rotation 42 of the moving part 30, and which is arranged to press radially against the braking spring so as to be able to vary, by a rotation about its axis of rotation, said radial pressure force exerted by the braking spring on the intermediate piece/washer.
  • the eccentric 20 is one of the two parts that maintain tension on the braking spring.
  • the tension on this spring is varied, allowing adjustment of the braking torque applied to the first moving part 30 (chronograph wheel) when it is subjected to a rotational driving torque.
  • This configuration is advantageous because it is not sensitive to vibrations and shocks.
  • a different radial force adjustment device is provided, specifically a device equipped with a pressure element that can be moved linearly.
  • FIG. 9 This illustrates another embodiment of the invention in which the braking spring 11 is straight (unconstrained).
  • This spring is rigidly fixed at one of its two ends to a fixed part 82, the angular positioning of which in the geometric plane is fixed, thus preventing any unintentional displacement or displacement due to impact.
  • the groove in the part 82, into which the end of the spring 11 is inserted, is oriented such that a median area of the spring exerts a radial pressure force F on the washer 8.
  • This spring then presents, between the fixing part 82 and the point of contact of the spring on the washer, a first convex curvature (as seen from the washer).
  • an eccentric is provided which, in this embodiment, is located on the same side of the braking spring as the washer 8, which forms the intermediate part between the braking spring and the shaft of the moving part concerned.
  • the braking spring 11 also exhibits a second convex curvature between said fulcrum and the eccentric 20, this second curvature being smaller than the first curvature because the radial force F is not zero.
  • the variant shown in the Figure 9 This defines a single-point support design, meaning the brake spring bears a single point on the washer, as previously defined.
  • the two-point design incorporates a star-shaped intermediate piece, for example, with four to six points, each slightly rounded.
  • the slightly convex brake spring constantly presses on two points of this intermediate star, exerting two forces that, at their central point, combine to create a single radial pressure force. In other words, the two forces generate two equal and opposite moments of force on the intermediate piece. It should also be noted that the braking system cannot be misaligned in the event of an impact.
  • FIGS 1 to 3 show the mechanical watch movement 2 with the braking device 6 previously mounted in a preliminary step before the assembly of the first moving part 30.
  • This assembly The preliminary design of the braking device 6 is advantageous. This is made possible in particular by the fact that the force exerted by the braking spring is radial and by the fact that the washer 8 is positioned above a pinion and a wheel 32 forming the first moving part and, in the example shown where the first moving part is a chronograph moving part, above a reset heart 34.
  • Figures 4 And 5 show the mechanical watch movement 2 after the assembly of the first mobile 30 in this movement and the braking device in a functional state.
  • the washer 8 is arranged on a support 4 (barrel bridge) which has a horizontally positioned stop surface 26 around the periphery of the washer, opposite the washer and diametrically opposite the bearing surface 25, so that the washer 8 and the braking spring 10 can be pre-assembled in the mechanical watch movement 2, before the assembly of the first moving part 30, with the washer bearing against the stop surface 26, as shown in the diagrams.
  • the stop surface 26 is defined by a lateral surface of a cavity 12 machined in the support 4, the washer being arranged in this cavity 12 open on the lower side of the movement (by definition, the analog display is on the upper side).
  • the stop surface 26 is arranged so that, following the prior assembly of the washer 8 and the braking spring 10, the central cylindrical opening of the washer has at least one overlapping area with the central circular opening of a barrel or tube 44, into which a portion of the shaft 36 of the first moving part 30 (chronograph moving part) is subsequently inserted, so that the shaft can, during the assembly of the first moving part in the mechanical watch movement 2, enter both central circular openings without initially having to exert a radial force on the washer.
  • the central cylindrical opening of washer 8 is entirely superimposed on the central circular opening of barrel 44.
  • the shaft 36 of the first moving part 30 is inserted into a barrel 44 which carries a display hand and is thus free to rotate, this barrel being pivoted within the mainplate 60 and the barrel bridge 4.
  • a barrel 44 which carries a display hand and is thus free to rotate
  • this barrel being pivoted within the mainplate 60 and the barrel bridge 4.
  • Inside the central opening of the barrel is arranged an internal bearing 46 in which an end portion 37 of the shaft 36 is pivoted.
  • This end portion, on which the chronograph hand 48 is mounted has a maximum diameter smaller than the diameter of the cylindrical and axial surface of revolution 35, which is ultimately located inside the central cylindrical opening 9 of the washer. This makes it particularly easier to insert the shaft 36 into the two central circular openings during the assembly of the chronograph moving part when the initial overlap of the two central circular openings, before the assembly of this chronograph moving part, is only partial.
  • the first moving part 30, forming a chronograph moving part in the embodiment shown, is pivoted by the upper bearing 46 and by a lower bearing 38 arranged in an opening in a bridge 40.
  • the washer 8 is no longer supported against the lateral wall 26 of the cavity 12 of the support 4, but rather, by its central cylindrical opening, it rests against the shaft 36 of the first moving part, more precisely against a surface of revolution 35, advantageously cylindrical and axial, of this shaft.
  • the barrel is pivoted between the barrel bridge 4, forming the support piece for the washer 8, and the plate 60.
  • the first moving part is driven in rotation intermittently, on command, by a second moving part 52 via a clutch wheel 54 mounted on a rocker 56, which is conventionally driven by a column wheel or a cam (disengagement schematically indicated by an arrow at the Figure 4 ).
  • the second mobile 52 includes a drive wheel which is incorporated into the gear train from the barrel to the escape wheel 58. This drive wheel here forms a small seconds wheel of the time display of the watch receiving the mechanical watch movement 2.
  • the present invention has been described in detail for a chronograph mobile 30, but the braking device of the invention can be provided for other mobiles of a mechanical watch movement, in particular for a small seconds mobile when this mobile is not included in the gear train from the barrel to the escape wheel 58.
  • the braking device 6 includes an eccentric 20 that allows for easy adjustment of the radial pressure force exerted by the braking spring on the intermediate piece/washer 8 and, via this washer, the radial force applied to the shaft 36 of the first moving part 30, as well as adjustment of the frictional torque applied to this first moving part.
  • the eccentric 20 allows for adjustment of the braking torque once the braking device is fully mounted in the mechanical watch movement, without having to remove the braking spring to slightly alter its initial shape.
  • the braking device 6 is such that it is protected against stresses which could damage it during the assembly of other parts of the mechanical watch movement, in particular during the assembly of the chrono mobile 30. During disassembly of the watch movement, and in particular of the first mobile 30, the braking device 6 can remain in place without its setting being modified.
  • the braking device allows the moment of force of the friction to be defined in advance in a relatively precise manner, given that the lateral surface 9 of the intermediate piece, in particular of the washer 8, has a height generally much greater than that of the braking spring, that the material of the intermediate piece / washer 8 can be selected and that the diameter of the surface of revolution, defining a cylindrical and axial surface, of the shaft 36 against which the intermediate piece / washer 8 presses is precisely determined.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
  • Braking Arrangements (AREA)
  • Electric Clocks (AREA)
  • Electromechanical Clocks (AREA)

Claims (15)

  1. Mechanisches Uhrwerk (2) umfassend ein Federhaus, ein mit einem mechanischen Oszillator gekoppeltes Hemmrad (58), ein Anzeigerad (30) mit einer Welle (36) zum Tragen eines Anzeigeorgans (48) sowie eine mit dem Anzeigerad gekoppelte Bremsvorrichtung (6), die eine Bremsfeder (10, 10A, 10B, 11) und ein zwischen der Bremsfeder und der Welle des Anzeigerads angeordnetes Zwischenstück (8, 68, 78) umfasst, wobei das Anzeigerad vom Federhaus in Drehung antreibbar ist, jedoch nicht Teil eines Räderwerks vom Federhaus zum Hemmrad ist, und wobei die Bremsfeder derart angeordnet ist, dass sie, sobald das Anzeigerad einem antreibenden Drehmoment unterliegt, über das Zwischenstück, gegen das diese Bremsfeder drückt, ein Bremsmoment auf das Anzeigerad ausübt; dadurch gekennzeichnet, dass das Zwischenstück und die Bremsfeder so angeordnet sind, dass das Zwischenstück im Normalbetrieb stationär und ohne Rotation bleibt; und dass das Zwischenstück eine Seitenfläche (9) aufweist, die gegen eine Mantelfläche (35) der genannten Welle drückt, und eine Auflagefläche (25), gegen die die Bremsfeder insgesamt eine Druckkraft in Richtung der genannten Welle ausübt, um zwischen der Seitenfläche und der Mantelfläche eine Reibkraft zu erzeugen, die das genannte Bremsmoment hervorruft.
  2. Mechanisches Uhrwerk nach Anspruch 1, dadurch gekennzeichnet, dass das Zwischenstück (8, 68, 78) eine ausschließlich radiale Anpresskraft auf die Welle (36) des Anzeigerads (30) ausübt.
  3. Mechanisches Uhrwerk nach Anspruch 1 oder 2, wobei die Welle eine Mittelachse (42) definiert, dadurch gekennzeichnet, dass die genannte Mantelfläche (35) zylindrisch und axial ausgerichtet ist und die genannte Seitenfläche (9) axial ausgerichtet ist.
  4. Mechanisches Uhrwerk nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Bremsfeder (10, 10A, 10B, 11) eine Drahtfeder oder eine Blattfeder ist, deren Längsachse in einer geometrischen Ebene liegt, die parallel zu einer allgemeinen Ebene (50) des Uhrwerks verläuft.
  5. Mechanisches Uhrwerk nach Anspruch 4, dadurch gekennzeichnet, dass die Bremsfeder (10, 10A, 10B, 11) so angeordnet ist, dass ein mittlerer Abschnitt dieser Bremsfeder die genannte Druckkraft auf die genannte Auflagefläche des Zwischenstücks (8, 68, 78) ausübt; und dass zwei Endabschnitte der Bremsfeder, die sich jeweils auf beiden Seiten des genannten mittleren Abschnitts befinden, gegen zwei voneinander beabstandete Bereiche (16, 20) des Uhrwerks abgestützt sind, sodass der mittlere Abschnitt die Druckkraft auf die genannte Auflagefläche ausübt.
  6. Mechanisches Uhrwerk nach Anspruch 5, dadurch gekennzeichnet, dass die Bremsfeder (10, 10A, 10B) nicht am Uhrwerk befestigt ist, sondern durch die genannten voneinander beabstandeten Bereiche (16, 20) des Uhrwerks unter Vorspannung gehalten wird, gegen die die genannten beiden Endabschnitte der Bremsfeder in zwei Richtungen in der genannten geometrischen Ebene drücken.
  7. Mechanisches Uhrwerk nach Anspruch 6, dadurch gekennzeichnet, dass das Zwischenstück und die Bremsfeder so ausgelegt sind, dass sich ihre relative Positionierung im Wesentlichen nicht im Zeitverlauf ändert, selbst dann nicht, wenn eine Längsverschiebung der Bremsfeder infolge einer in der allgemeinen Ebene des Uhrwerks einwirkenden Beschleunigung auftritt.
  8. Mechanisches Uhrwerk nach einem der vorstehenden Ansprüche 5 bis 7, dadurch gekennzeichnet, dass es einen Exzenter (20) umfasst, dessen Drehachse senkrecht zu der genannten geometrischen Ebene verläuft und der derart eingerichtet ist, dass er gegen die Bremsfeder (10, 10A, 10B, 11) drückt, um durch Drehung um seine Drehachse die genannte Anpresskraft zu variieren, die die Bremsfeder auf das Zwischenstück (8, 68, 78) ausübt.
  9. Mechanisches Uhrwerk nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass das Zwischenstück eine Scheibe (8) mit einer zentralen Öffnung ist, durch die die Welle (36) des Anzeigerads geführt ist, wobei die genannte Seitenfläche (9) dieser Scheibe durch eine zylindrische Fläche ihrer zentralen Öffnung gebildet ist.
  10. Mechanisches Uhrwerk nach Anspruch 9, dadurch gekennzeichnet, dass die Scheibe (8) an ihrem Umfang eine Nut (24) aufweist, die die genannte Auflagefläche (25) bildet und in die zumindest teilweise ein Abschnitt der Bremsfeder (10) eingeführt ist, der die genannte Druckkraft in Richtung der genannten Welle ausübt.
  11. Mechanisches Uhrwerk nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass das Zwischenstück (8) auf einem Träger (4) angeordnet ist, der im Umfangsbereich des Zwischenstücks eine Anschlagfläche (26) aufweist, die dem Zwischenstück horizontal gegenüberliegt und der genannten Auflagefläche (25) diametral gegenüberliegt, sodass das Zwischenstück und die Bremsfeder vorab im mechanischen Uhrwerk montiert werden können, vor der Montage des Anzeigerads (30), wobei das Zwischenstück an der Anschlagfläche anliegt.
  12. Mechanisches Uhrwerk nach Anspruch 11, dadurch gekennzeichnet, dass die Anschlagfläche (26) derart ausgebildet ist, dass nach der Vormontage des Zwischenstücks (8) und der Bremsfeder (10) die zylindrische zentrale Öffnung des Zwischenstücks mit der zylindrischen zentralen Öffnung eines drehbar gelagerten oder festen Kanonrohrs (44) bzw. Rohrs, in das ein Teil der Welle (36) des Anzeigerads (30) eingeführt ist, mindestens eine Überdeckungszone aufweist, sodass die Welle beim Einbau des Anzeigerads in das mechanische Uhrwerk in beide zentralen kreisförmigen Öffnungen eintreten kann, ohne anfänglich eine radiale Kraft auf das Zwischenstück ausüben zu müssen.
  13. Mechanisches Uhrwerk nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass mindestens ein Teil der Welle (36), der die genannte Mantelfläche (35) definiert, aus Stahl besteht oder aus einer Kupferlegierung gebildet ist, und dass mindestens ein Teil des Zwischenstücks (8), der die genannte Seitenfläche (9) definiert, jeweils aus einer Kupferlegierung oder aus Stahl besteht.
  14. Mechanisches Uhrwerk nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass mindestens ein Teil der Welle (36), der die genannte Mantelfläche (35) definiert, aus Stahl besteht oder aus einer Kupferlegierung gebildet ist, und dass mindestens ein Teil des Zwischenstücks (8), der die genannte Seitenfläche (9) definiert, aus Polymeren besteht.
  15. Mechanisches Uhrwerk nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass mindestens ein Teil der Welle (36), der die genannte Mantelfläche (35) definiert, aus Stahl besteht oder aus einer Kupferlegierung gebildet ist, und dass mindestens ein Teil des Zwischenstücks (8), der die genannte Seitenfläche (9) definiert, aus einer Keramik, insbesondere Rubin oder Zirkonoxid, besteht oder aus einem Gold- oder Nickel-haltigen Material gebildet ist, das eine Außenbeschichtung bildet, welche das Zwischenstück zumindest bereichsweise überzieht.
EP24163635.6A 2023-05-10 2024-03-14 Mechanisches uhrwerk, das ein bewegliches element umfasst, das ein anzeigeelement mit einer bremsvorrichtung umfasst Active EP4462193B1 (de)

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DE6800934U (de) 1968-10-04 1969-09-25 Junghans G M B H Fa Geb Vorrichtung an einem uhrwerk zum bremsen einer getriebewelle
CH1003573A4 (de) 1973-07-10 1976-04-15
JP2006242793A (ja) * 2005-03-04 2006-09-14 Seiko Epson Corp 時計
CH709154A1 (fr) * 2014-01-16 2015-07-31 Richemont Int Sa Mouvement et pièce d'horlogerie mécanique comprenant un mécanisme de chronographe.
EP2977829B1 (de) * 2014-07-24 2017-07-12 ETA SA Manufacture Horlogère Suisse Anordnung mit beweglichem Bremselement einer Uhr
JP6452728B2 (ja) * 2015-01-05 2019-01-16 シチズン時計株式会社 機械式時計のムーブメント
EP3396470B1 (de) * 2017-04-24 2020-01-01 ETA SA Manufacture Horlogère Suisse Mechanische bremsvorrichtung für drehteil einer uhr
EP3667431B1 (de) * 2018-12-13 2025-06-04 Montres Breguet S.A. Mobile anzeigeeinheit einer uhr mit reibungsregulierungsmechanismus
CH716957A2 (fr) * 2019-12-16 2021-06-30 Eta Sa Mft Horlogere Suisse Dispositif de guidage pour afficheur d'horlogerie.
JP7467390B2 (ja) * 2021-06-15 2024-04-15 シチズン時計株式会社 指針のふらつき低減構造
EP4160322B1 (de) * 2021-09-29 2025-06-25 ETA SA Manufacture Horlogère Suisse Bremsfeder für trägerwelle einer anzeige, uhrwerk mit dieser bremsfeder und einbauverfahren dieser bremsfeder

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