WO2013056706A1 - Système oscillant pour mouvements de montre mécaniques - Google Patents

Système oscillant pour mouvements de montre mécaniques Download PDF

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Publication number
WO2013056706A1
WO2013056706A1 PCT/DE2012/100327 DE2012100327W WO2013056706A1 WO 2013056706 A1 WO2013056706 A1 WO 2013056706A1 DE 2012100327 W DE2012100327 W DE 2012100327W WO 2013056706 A1 WO2013056706 A1 WO 2013056706A1
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WO
WIPO (PCT)
Prior art keywords
spring
region
coil spring
stabilization
spiral
Prior art date
Application number
PCT/DE2012/100327
Other languages
German (de)
English (en)
Inventor
Petra Damasko
Original Assignee
Petra Damasko
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE201210100817 external-priority patent/DE102012100817B4/de
Application filed by Petra Damasko filed Critical Petra Damasko
Publication of WO2013056706A1 publication Critical patent/WO2013056706A1/fr

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/066—Manufacture of the spiral spring

Definitions

  • the invention relates to a vibration system for mechanical movements.
  • the balance comprises a vibrating body, which is mounted pivotably about an axis of rotation by means of a balance shaft. Further, a vibrating or spiral spring or balance spring is provided, which forms the oscillatory and clocking system together with the mass of the oscillating body.
  • the active spring length is included the length of the coil spring which is effective during swinging, that is subject to elastic deformation and extends between the inner coil spring end and the outer breakpoint of the coil spring.
  • the inner coil spring end is located at the point where the coil spring has a width radial to the spring axis that is equal to or substantially equal to the width of all turns (common turn width).
  • tolerances can not be excluded. This applies, as stated, to a greater extent for spiral springs of silicon, which are provided on their surfaces to achieve the necessary strength and / or temperature independence with a coating of silicon oxide. As a rule, this coating takes place by thermal oxidation.
  • a possible constant and permanently unchanged vibration behavior of a vibration system represents the ultimate goal in the field of mechanical movements.
  • the "oscillation range" of the helical spring is the spiral length of the spring in which the oscillation proceeds unhindered. - -
  • the present invention provides a vibrating system for mechanical timepieces comprising a vibrating body, a balance shaft pivotally mounted about an axis, and a coil spring having a total spring length, wherein the total spring length is composed of an inner vibration region having a vibration spring length and an outer stabilizing region having a stabilizing spring length.
  • the coil spring is connected to the balance shaft with a coil spring attachment portion and encloses the balance shaft with the coil spring attachment portion.
  • the coil spring is held or clamped in the outer stabilization region at a spring-holding point, the total spring length extending from an inner end of the inner oscillation region to the outer spring-holding point.
  • the spiral spring has an average height h sc in its inner oscillation area parallel to the axis of the balance spring coinciding with the axis of the balance spring, and has an average width b sc radial to the axis of the spiral spring.
  • the spiral spring has in the outer stabilization region parallel to the axis of the coil spring an average height hst which is at least 1% less than the average height h sc in the inner oscillation range.
  • the spiral spring has an average width bst in the outer stabilization region radially to the axis of the spiral spring, which is at least 1% larger than the average width b sc in the inner vibration region.
  • the present invention is based on the finding that an improved oscillation behavior is not necessarily achieved by an increased mass in the stabilization region of the spiral spring, but rather by an increase in the area moment of inertia of the spiral spring in its stabilization region.
  • Such an increase in the area moment of inertia can be achieved in a simple manner by means of a reduced height and increased width of the spiral spring in comparison with the oscillation range of the spiral spring in the stabilization region. Since the increase of the width with the third power enters into the calculation of the area moment of inertia and the decrease of the height only has a linear effect, the spiral spring can be designed so that an increase of the area moment of inertia without mass increase is possible.
  • the area moment of inertia (FT) can be calculated for a rectangular cross section of the coil spring as follows, where h denotes the height of the spiral spring and b the width of the spiral spring:
  • the height is reduced by 1% with a simultaneous increase in the width of the coil spring by 1% Increase of the second moment of area by 2%.
  • the ratio of the mass of the stabilization area to the mass of the oscillation area results as follows: - -
  • the average height h st is obtained by reducing the height by 1% while increasing the width of the coil spring by 1% no change in mass.
  • the inventive change in the geometric cross section of the coil spring in the stabilization region with respect to the vibration region thus an increase in the area moment of inertia without increasing the mass is possible.
  • the present invention relates to any form of coil spring in which a reduction in height and an increase in the width in the claimed type is made. This also includes embodiments which, despite the reduction in height, experience an increase in mass due to the increase in the width in the stabilization region. - -
  • average height or the average width of a helical spring is understood to mean the mean value of the spring length that is normalized over the respective spring length or the varying width of a helical spring.
  • Coil springs are usually manufactured for manufacturing reasons with a constant height and a constant width, but which may differ between the vibration range and the stabilization range. For various reasons, however, it may happen that a spiral spring has varying height or varying width in the oscillation range and / or in the stabilization range.
  • the total spring length is composed of the inner vibration region and the outer stabilization region.
  • the overall spring length of the coil spring extends from the inner coil spring end to the outer spring stop point.
  • the inner end of the vibration region is located at the point where the oscillation region of the coil spring merges with the coil spring attachment section which serves to fix the coil spring to the balance shaft.
  • the outer spring retention point is determined either by a fixed spring retention point or by the position of a recoiler.
  • the outer stabilizing portion corresponds to a portion of the coil spring extending from the spring-holding point toward the oscillation portion of the coil spring, the boundary between the stabilizing portion and the oscillating portion being set by the average height h st of the coil spring being at least 1% smaller in its stabilizing range the average height h sc of the coil spring in its inner oscillation range and at the same time the average width b st of the spiral spring in their - -
  • Stabilization is at least 1% larger than the average width b sc of the coil spring in the inner vibration range.
  • the boundary between the stabilization area and the oscillation area is immediately apparent because of a discontinuity in height and a discontinuity in width corresponding to one step.
  • the boundary between stabilization area and oscillation area can be determined by the person skilled in the art with the aid of simple measurements.
  • the point at which the average height of the area adjoining the spring support point in the direction of the oscillation area is at least 1% lower can be calculated by a simple mathematical evaluation as the height of the area adjoining the coil spring attachment portion toward the outer stabilization area. Also, the point at which the average width of the area adjoining the spring stop point in the direction of the oscillation area is larger by at least 1% than the width of the area adjoining the coil spring attachment section toward the outer stabilization area can be calculated. The point from which both conditions are met is the boundary between "inner oscillation range” and "outer stabilization range”.
  • the limit for each coil spring can be determined unambiguously by a measurement that is easy to carry out for the person skilled in the art and can be easily evaluated.
  • the corresponding limit can be determined by calculating the point at which the average height or width of the area adjoining the spring stop point in the direction of the oscillation area is at least 10% or one of corresponding lower preferred value - less than or greater than the height or width of the adjoining the inner coil spring attachment portion in the direction of the externa ßeren stabilization region range.
  • the coil spring in the outer stabilization region has an average height h st which is at least 2% or 3% or 4% or 5% or 6% or 7% or 8% or 9% or 10% less than the average height h sc in the inner oscillation range.
  • the spiral spring in the outer stabilization region has an average height h st which is at least 12% or 14% or 16% or 18% or 20% or 22% or 24% or 25% less than the average height h sc in the interior vibration region.
  • the spiral spring in the outer stabilization region has an average height h st which is at least 30% or 35% or 40% or 45% or 50% less than the average height h sc in the inner oscillation range.
  • the spiral spring has a constant height h sc in the inner oscillation range.
  • the spiral spring has a constant height h st in the outer stabilization region.
  • a constant height brings with it manufacturing advantages, since, for example, a smaller number of etching masks is used in etching processes.
  • the spiral spring in the outer stabilization region radially to the axis of the coil spring has an average width b st , which is at least 2% or 3% or 4% or 5% or 6% or 7% or 8% or 9% or 10% greater than the average width b sc in the inner oscillation range.
  • the coil spring in the externa ßeren stabilization region has an average width - -
  • coil spring in the outer stabilization region has an average width b st which is at least 30% or 35% or 40% or 45% or 50% greater than the average width b sc in the inner oscillation range.
  • an additional mass provided in the outer stabilization region improves the oscillatory behavior of the spiral spring. By broadening the spring in the stabilization region, such an additional mass can be provided, although the spring in this region has a reduced height compared to the inner vibration region.
  • the width, which has the coil spring in the stabilization region about twice the width correspond to the coil spring has au outside the stabilization region. If this spiral spring has a height in the stabilization region which corresponds approximately to half the height which the spiral spring has outside the stabilization region, then the geometric cross-sectional shape of the spiral spring is changed, but its mass per unit length remains constant. At the same time, however, the area moment of inertia is increased, whereby the desired optimal behavior of the spiral spring in the oscillating state of the oscillatory system, i. the avoidance of the displacement of the coil spring results.
  • the stabilization of the oscillatory behavior of the spiral spring is further improved if at least one stabilization factor for the spiral spring, namely the area inertia stabilization factor (r) FT) and / or the spring constant stabilization factor (r) k) is described below Way is chosen.
  • the coil spring consists of an inner oscillation area and an outer stabilization area in which the height - -
  • the inner vibration range extends over an angle range of 0 ° to 9A, i. from the inner end of the vibration region to the beginning of the outer stabilization region.
  • the externa ßere stabilization range is in the angular range 9A to 9E and extends to the outer spring support point.
  • the slope of the loop geometry can be of any functional connection.
  • a helical spring with a linear pitch is used by way of example.
  • the width, the material used and the cross-sectional geometry within the oscillation range and the stabilization range are freely selectable with the proviso that the coil spring in the outer stabilization region has an average height hst parallel to its axis which is at least 1% less than the average height h sc in the inner oscillation range.
  • the radius r (9) of the spiral spring is a function of the angle 9 and is generally defined by the following relationship:
  • the angle 9A which describes the beginning of the stabilization region and the
  • Angle 9E which determines the overall length of the coil spring, can be freely selected. From empirical measurements ideal values for achieving a stable behavior were determined.
  • angle values 9A and 9E are assigned the associated lengths LA and LE.
  • LA is the total spring length up to the angle 9A with the relationship
  • LE is the spiral length or length of the coil spring up to the angle 9E, with the relationship
  • FT (I) is below the course of the moment of inertia as a function of the length of the coil spring and E is below the modulus of elasticity of the material used for the coil spring.
  • the parameter values are determined so that the respective physical size of the stabilization range from LA (9A) to LE (9E) into
  • the reference coil spring is a spring that - -
  • the determined stabilization factor r) FT and n.k. is thus influenced only by the stabilizing measures in the outer region of the spiral spring.
  • the stabilization factor r) FT represents the ratio of the courses of the moment of inertia distributions FT (I) as a function of the length of the spiral spring in the section of the stabilization region to the vibration region and this in the overall comparison to the reference coil spring:
  • FT (I) is the course of the area moment of inertia as a function of the length I
  • FTn (l) is the course of the area moment of inertia of the reference coil spring as a function of the spring length (I).
  • the stabilization factor r) FT is chosen to be in the range 10 ⁇ r) FT ⁇ 65. - -
  • the stabilizing factor nk is the ratio of the spring constant of the stabilizing angle range 9A to 9E to the spring constant of the oscillation range 0 to 9A and this in comparison to the ratio of the spring constant in the analog angular ranges of the reference coil spring:
  • kSchwing ⁇ 0 - M) sprial are k stabi
  • the stabilization factor nk is chosen such that it lies in the range 1, 5 .s nk ⁇ 65, preferably in the range 1, 5 ⁇ nk ⁇ 25.
  • the average height h sc and the average width b sc of the coil spring in its inner oscillation range and the average height h st and the average width b st of the coil spring in its outer stabilization region are coordinated such that a
  • Area moment of inertia stabilization factor has a value lying in a predetermined setpoint range associated with the area inertia stabilization factor (nFT) and / or a spring constant stabilization factor (nk) having a predetermined setpoint area associated with the spring constant stabilization factor (nk), - -
  • the area moment of inertia stabilization factor being represented by the ratio of a first quotient to a second quotient, the first quotient being the ratio of the area moment of inertia of the outer stabilization area of the spiral spring to the area moment of inertia of the inner oscillation area of the spiral spring and the second quotient the ratio of the area moment of inertia of one corresponding spring length to the area moment of inertia of the spring portion corresponding spring length of a reference coil spring, according to the formula
  • FT (I) the course of the moment of area moment of the spiral spring as a function of the spring length (I) and FTn (l) the course of the moment of inertia of the reference spring as a function of spring length (I), wherein the setpoint of the area moment of inertia (nFT) setpoint range between 10 and 65
  • the spring constant stabilizing factor (nk) is represented by the ratio of a first quotient to a second quotient, the first quotient being the ratio of the spring constant of the outer stabilizing portion of the coil spring to the spring constant of the inner oscillating portion of the spiral spring and the second quotient the ratio of Spring constants of a spring length corresponding to the stabilization region to the spring constant of a spring length of a reference coil spring corresponding to the vibration region, according to the formula - -
  • it is at the outer spring support point to a fixed Ansteckddling or it is the externa ßere spring holding point formed by a back.
  • the stabilization region preferably extends over an angular range of 10 ° to 360 °, particularly preferably from 20 ° to 270 °, particularly preferably from 30 ° to 180 °, very particularly preferably from 40 ° to 100 ° .
  • the stabilization region extends over an angular range of at least 10 °, particularly preferably of at least 20 °, particularly preferably of at least 30 °, very particularly preferably of at least 40 °, of at least 60 °, at least 90 ° or at least 120 ° ,
  • the angular range extends from the outer spring-holding point in the direction of the oscillation range of the spiral spring.
  • the spiral spring preferably consists of a non-metallic material, preferably of diamond or of silicon with a coating of silicon oxide.
  • the present invention also includes a mechanical timepiece with a mechanical vibration system, wherein the vibration system is configured as described above.
  • the present invention also includes a method of adjusting a mechanical movement oscillating system as described above comprising the step of adjusting the total spring length (LE) by changing the outer spring stopping point.
  • the externa ßere spring holding point is after setting fixed Ansteckddling.
  • the outer spring holding point is adjusted with a gearing.
  • FIG. 1 shows by way of example a perspective view of a vibration system for mechanical watches
  • FIG. 2 shows a section along a plane receiving the axis of the balance-wave shaft through the oscillating system according to FIGS
  • Fig. 3 by way of example a perspective side view of the exempted
  • FIGS. 1 to 3 For a better understanding of the present invention, a vibrating system for mechanical movements known from the prior art will be described in connection with FIGS. 1 to 3.
  • the oscillating system 1 comprises a vibrating body in the form of a flywheel 2, a balance shaft 3 and a coil spring 4.
  • the flywheel 2 consists of an outer circular ring section 2.1, which is connected via a plurality of spokes 2.2 with a hub section 2.3.
  • the hub portion 2.3 has a deviating from the circular, central through hole, in which an associated shaft portion 3 'of the balance shaft 3 is added, the concentric Au chseite forms a positive connection with the hub portion 2.3 of the flywheel.
  • the flywheel is rotatably connected to the balance shaft 3.
  • several inertia 2.4 are attached at the rotation center of the flywheel facing inside of the externa ßeren circular ring section 2.1 several inertia 2.4 are attached.
  • the balance-wheel shaft 3 also has an upper and lower free end 3.1, 3.2, which taper in a pointed manner and are received for the rotatable mounting of the balance-wheel shaft 3 about its axis UA in correspondingly formed upper and lower bearing units.
  • an upper bearing unit is shown by way of example.
  • the axis UA of the balance shaft 3 is thus at the same time the axis of rotation of the flywheel and the coil spring axis.
  • the coil spring 4 consists of a preferably annular, inner coil spring attachment section 4.1 and an outer spiral spring end section 4.2. In between there are several spiral spring ring sections 4.3, which extend in a plane perpendicular and preferably concentric with the spiral spring axis, which coincides with the axis UA of the balance shaft 3.
  • the preferably annular, inner coil spring mounting portion 4.1 is rotatably connected to the balance shaft 3, preferably glued and / or by positive engagement.
  • Die Garar Ben 5 comprises at least one holding arm 6 and a holding element 7 which is slidably mounted in the region of the externa ßeren free end of the support arm 6 along the longitudinal axis LHA of the lever arm 6.
  • the holding arm 6 has an inner retaining arm 6.1 and an externa ßeres retaining arm
  • the inner retaining arm 6.1 forms an open circular ring and in the region of the externa ßeren retaining arm 6.2 6.2 an elongated guide recess 6.3 is provided.
  • the elongated guide recess 6.3 is provided for the variable attachment of the holding element 7 on the support arm 6.
  • the inner retaining arm 6.1 is about unspecified holding means which can accommodate the upper and lower bearing units for rotatable mounting of the balance shaft 3, rotatably secured, in such a way that the open circular ring of the inner armrest 6.1 surrounds the axis UA of the balance shaft 3 concentric ,
  • the holding element 7 has a substantially cylindrical, elongated base body 7.1 with an upper and lower end face 7.1 1, 7.12 and a longitudinal axis LHE, which has a 7.15 opened to the upper end face blind hole 7.2 with an internal thread for receiving a screw 8.
  • a screw 8 By means of the screw 8, which through the elongated guide recess
  • the holding member 7 is firmly screwed to the support arm 6, in such a way that the longitudinal axis LHA of the support arm 6 and the longitudinal axis LHE of the holding member 7 are perpendicular to each other.
  • a plane receiving the longitudinal axis LHE of the main body 7.1 divides the guide recess 7.3 approximately into two opposite, equal halves of the fork-shaped lower free end of the holding element 7.
  • the coil spring center is adjustable, and preferably such that the Spiralfederringabête 4.3 each have the same distance from one another and extend concentrically about the axis UA.
  • FIG. 4 shows, in a detail view and a top view, a spiral spring 4 of the mechanical vibration system according to an embodiment of the invention.
  • the coil spring 4 in the illustrated embodiment is e.g. of a raw material (wafer) of silicon, for example of polycrystalline silicon, e.g. made of a starting material obtained by epitaxial deposition, e.g. using a masking etch process, such that the integrally formed coil spring 4 having a plurality of turns 9 is fastened to the balance shaft 3 with the inner spiral spring attachment section 4.1 and is designed with an outer stabilization region LS.
  • the externa ßere stabilization region LS is in the region of the outer winding and extends over an angular range ⁇ of 100 °.
  • the stabilization region LS is formed in the illustrated embodiment in that the spiral spring 4 has an enlarged width radially to its spring axis and a reduced height parallel to its spring axis.
  • the stabilizing area LS extends from the spring stopping point 13 to the beginning of the oscillation area, wherein the boundary between stabilizing area and oscillation area is to be determined as defined above.
  • Stabilization area LS changed cross-sectional geometry is achieved an increase in the area moment of inertia and prevents displacement of the coil spring 4 when swinging the vibration system.
  • the active length extends from the inner end connected to the coil spring attachment section 4.1 and indicated at 12 in FIG. 4 to the spring stop 13. In the embodiment shown in FIGS Connection of the outer coil spring sections 4.3 formed with the support member 7.
  • the frequency of the vibration system is set, for example, by appropriate choice of the mass of the flywheel 2 provided on the flywheel 2.4.
  • flywheel masses 2.4 are preferably used, which have a different height parallel to the axis UA of the balance shaft 3 in order to achieve a different mass in the axial direction.
  • the spiral spring 4 is made of silicon in a masking-etching process.
  • the production method eg masking-etching method
  • the spring stop point is positioned in the stabilization region, that an optimal vibration behavior is achieved.
  • the length ratio of stabilization region to vibration region and an optimal amplitude for the vibration of the vibrating body 2 can be achieved, for example in an angular range between 280 ° and 330 °, again in spite of tolerances of the spring or driving force housed in a spring housing drive spring.
  • a spring-holding point 13 would be fixed after setting.
  • a so-called gearers 15 which is essentially formed by a pivotable about the axis of the balance shaft 3 lever 16.
  • the lever 16 has a receptacle 17 formed, for example, by two pins, in which the spiral spring 4 engages and thus forms the spring-holding point.
  • the coil spring 4 is connected at 18 fixed to a circuit board or a bearing plate.
  • the receptacle 17 of the reminders 15 forms a solid spring support point.
  • the spring-holding point in the stabilization region LS can be set so that an optimum ratio of the length of the stabilization region to the length of the oscillation region and thus optimum oscillation behavior is achieved.
  • the coil spring 4 shown in Figure 5 has a total of 10 turns and an externa ßeren stabilization region LS, which in turn adjoins the length LA of the inner oscillation range to externa ßeren spring holding point, which determines the total length of the coil spring 4.
  • the stabilization region LS extends over an angle ⁇ of about 100 ° and consists of a subsequent to the length LA section 1 1 .1 with decreasing height and increasing width, from an adjoining section 1 1 .2 with constant or substantially constant height and width, from a section 1 1 .3, at which towards the outer end 4.4 out the height increases and the width decreases, and a section 1 1 .4, which extends up to the through the reminder 15 formed spring holding point extends.
  • the sections 1 1 .1 and 1 1 .3 each extend in the spiral spring 4 over an angular range of about 15 °.
  • the middle section 1 1 .2 has a larger angular range of about 30 ° compared to the sections 1 1 .1 and 1 1 .3.
  • the spiral spring 4 has a constant or substantially constant width b sc and a constant or substantially constant height h sc in the inner oscillation range.

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  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
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Abstract

L'invention concerne un système oscillant pour des mouvements de montre mécaniques, comprenant un corps oscillant (2), un axe de balancier (3) monté pivotant autour d'un axe UA et un spiral (4) possédant une longueur totale de ressort LE qui se compose d'une zone d'oscillation intérieure présentant une longueur de ressort d'oscillation LA et d'une zone de stabilisation extérieure présentant une longueur de ressort de stabilisation LS. Le spiral (4) est raccordé à l'axe de balancier (3) par un partie de fixation de spiral (4.1) et entoure l'axe de balancier (3). Le spiral (4) est maintenu ou serré dans la zone de stabilisation extérieure en un point de maintien de ressort (13), la longueur totale de ressort LE s'étendant de l'extrémité intérieure (12) de la zone d'oscillation jusqu'au point de maintien de ressort extérieur (13). Le spiral (4) présente dans sa zone d'oscillation intérieure, parallèlement à l'axe du spiral coïncidant avec l'axe UA de l'axe de balancier, une hauteur moyenne hsc et, radialement à l'axe du spiral, une largeur moyenne bsc. Le spiral (4) présente dans la zone de stabilisation extérieure, parallèlement à l'axe du spiral, une hauteur moyenne hst inférieure d'au moins 1 % à la hauteur moyenne hsc dans la zone d'oscillation intérieure. Le spiral (4) présente en outre dans la zone de stabilisation extérieure, radialement à l'axe du spiral, une largeur moyenne bst supérieure d'au moins 1 % à la largeur moyenne bsc dans la zone d'oscillation intérieure.
PCT/DE2012/100327 2011-10-21 2012-10-19 Système oscillant pour mouvements de montre mécaniques WO2013056706A1 (fr)

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
DE102011116567.7 2011-10-21
DE102011116567 2011-10-21
DE102011055069.0 2011-11-04
DE102011055069 2011-11-04
DE102011055637 2011-11-23
DE102011055637.0 2011-11-23
DE102012100280.0 2012-01-13
DE102012100280 2012-01-13
DE102012100817.5 2012-02-01
DE201210100817 DE102012100817B4 (de) 2012-01-13 2012-02-01 Verfahren zum Einstellen eines Schwingsystems für mechanische Uhrwerke, Schwingsystem und mechanische Uhr
DE202012103893.5 2012-10-11
DE201220103893 DE202012103893U1 (de) 2011-10-21 2012-10-11 Schwingsystem für mechanische Uhrwerke

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013106505B3 (de) * 2013-06-21 2014-07-17 Christoph Damasko Schwingsystem für mechanische Uhrwerke
WO2014203085A1 (fr) 2013-06-21 2014-12-24 Damasko Uhrenmanufaktur KG Système oscillant pour mouvements d'horlogerie mécaniques, procédé de production d'un spiral et spiral
WO2014203086A1 (fr) 2013-06-21 2014-12-24 Damasko Uhrenmanufaktur KG Système oscillant pour mouvements d'horlogerie mécaniques, spirals et leur procédé de production
DE102013110090A1 (de) 2013-09-13 2015-03-19 Damasko Uhrenmanufaktur KG Schwingsystem für mechanische Uhrwerke

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
CH708429A1 (fr) 2013-08-19 2015-02-27 Manuf Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle S A Spiral pour organe réglant de montre mécanique, organe régulateur muni d'un tel spiral, et procédé de réalisation d'un tel spiral.

Citations (3)

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Publication number Priority date Publication date Assignee Title
EP1431844A1 (fr) * 2002-12-19 2004-06-23 SFT Services SA Assemblage pour organe régulateur d'un mouvement d'horlogerie
CH698142B1 (fr) * 2004-07-02 2009-05-29 Nivarox Sa Spiral à courbe extérieure rigidifiée par déformation.
DE102008061182A1 (de) 2008-12-04 2010-06-10 Konrad Damasko Verfahren zum Herstellen eines Mikrobauteils

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1431844A1 (fr) * 2002-12-19 2004-06-23 SFT Services SA Assemblage pour organe régulateur d'un mouvement d'horlogerie
CH698142B1 (fr) * 2004-07-02 2009-05-29 Nivarox Sa Spiral à courbe extérieure rigidifiée par déformation.
DE102008061182A1 (de) 2008-12-04 2010-06-10 Konrad Damasko Verfahren zum Herstellen eines Mikrobauteils

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013106505B3 (de) * 2013-06-21 2014-07-17 Christoph Damasko Schwingsystem für mechanische Uhrwerke
WO2014203085A1 (fr) 2013-06-21 2014-12-24 Damasko Uhrenmanufaktur KG Système oscillant pour mouvements d'horlogerie mécaniques, procédé de production d'un spiral et spiral
WO2014203086A1 (fr) 2013-06-21 2014-12-24 Damasko Uhrenmanufaktur KG Système oscillant pour mouvements d'horlogerie mécaniques, spirals et leur procédé de production
DE102013110090A1 (de) 2013-09-13 2015-03-19 Damasko Uhrenmanufaktur KG Schwingsystem für mechanische Uhrwerke

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