WO2013056706A1

WO2013056706A1 - Oscillating system for mechanical clock movements

Info

Publication number: WO2013056706A1
Application number: PCT/DE2012/100327
Authority: WO
Inventors: Petra Damasko
Original assignee: Petra Damasko
Priority date: 2011-10-21
Filing date: 2012-10-19
Publication date: 2013-04-25
Also published as: DE202012103893U1

Abstract

The invention relates to an oscillating system for mechanical clock movements, comprising an oscillating body (2), a balance staff (3) mounted pivotably about an axis UA, and a spiral spring (4) having an overall spring length LE, wherein the overall spring length LE is made up of an inner oscillation region having an oscillating spring length LA and an outer stabilisation region having a stabilising spring length LS. The spiral spring (4) is connected by a spiral spring fastening portion (4.1) to the balance staff (3) and surrounds the balance staff (3). The spiral spring (4) is retained or gripped in the outer stabilisation region on a spring retaining point (13), wherein the overall spring length LE extends from the inner end (12) of the oscillation region to the outer spring retaining point (13). In the inner oscillation region, the spiral spring (4) has an average height h_sc parallel to the axis of the spiral spring, which axis coincides with the axis UA of the balance staff, and has an average width b_sc radially with respect to the axis of the spiral spring. In the outer stabilisation region, the spiral spring (4) has, parallel to the axis of the spiral spring, an average height h_st that is at least 1 % less than the average height h_sc in the inner oscillation region. Moreover, in the outer stabilisation region the spiral spring (4) has, radially with respect to the axis of the spiral spring, an average width b_st that is at least 1 % greater than the average width b_sc in the inner oscillation region.

Description

Oscillation system for mechanical movements

Technical area

The invention relates to a vibration system for mechanical movements.

State of the art

Oscillating systems for mechanical movements, especially for watches, are referred to in the art as a balance. 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.

DE 10 2008 061 182 A1 discloses the production of oscillating or spiral springs made of silicon, in particular of polycrystalline silicon and of silicon carbide. When using such coil springs to form a mechanical vibration system for mechanical movements, tolerances can occur within the scope of the production, which have a disadvantageous effect on the vibration behavior of the mechanical vibration system.

It is also known to form the oscillating or spiral spring of a mechanical oscillating system in the area of the externa ßeren turn to create an additional mass or leveling compound with a thickening in order to avoid an oscillating displacement of the coil spring during oscillation of the vibrating system. To achieve this effect, an optimal balance of the mass weight of the thickening in relation to the total mass weight of the active spring length of the coil spring is necessary. 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). In the manufacture of coil springs 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.

Presentation of the invention

This is where the invention starts. It will be shown a vibrating system for mechanical movements, with the despite manufacturing tolerances of the coil spring an improved vibration behavior of the coil spring is achieved. This object is achieved by the vibration system for mechanical movements according to claim 1. Further advantageous aspects, details and embodiments of the invention will become apparent from the dependent claims, the description and the figures.

For the purposes of the invention, 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. At the same time, 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:

FT = h ^* b ³

DFT

dFT _Λ7 , dFT,

& t T = - * An + AB

Oh OD

At constant mass:

This results in the percentage change to:

& FT _ & b

FT b

or

Thus, if the height of the coil spring decreases by 1% and the width of the coil spring increases by 1%, the area moment of inertia increases by 2% with constant mass. - -

This result can be confirmed by a simple calculation of the effects of a reduction of the height of the coil spring by 1% and an increase of the width of the coil spring by 1% on the area moment of inertia:

For the oscillation range results for the area moment of inertia:

FT, For the stabilization range results for the area moment of inertia:

FT, ³

According to the invention, the spiral spring has an average height h _st parallel to the axis of the helical spring in the outer stabilization region, which is at least 1% smaller than the average height h _sc in the inner vibration region, that is to say: h _st = 0.99 ^■ h _sc . At the same time, the spiral spring has an average width b _st 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, from which follows: b _st = 1, 01 ^■ b _sc .

For the ratio of the area moments of inertia, this results in:

FT _st / FT _SC = (h _st -b _st ³ ) / (hsc-b _s c ³ ) = (0.99-h _sc - (1, 01 -b _sc ) ³ ) / (h _sc -b _sc ³ ) = 0.99-1, 01 ³ = 1, 02

Irrespective of the concrete values for the average height h _st , the average height h _sc , the average width b _st and the average width b _sc , 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%.

If the masses of the two areas are normalized to a defined length, the ratio of the mass of the stabilization area to the mass of the oscillation area results as follows: - -

m _st / m _sc = (h _st -b _st ) / (h _sc -bsc) = (0.99 -h _sc -1, 01 -b _S c) (hsc-b _S c) = 0.99-1 , 01 = 1, 00

Again, irrespective of the concrete values for the average height h _st , the average height h _sc , the average width b _st and the average width b _sc are 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.

As a further simple example, let us mention a coil spring in which the width in the stabilization region is increased by 100% (corresponding to a factor of 2) while the height is reduced by 50% (corresponding to a factor of 0.5). For the stabilization section of this spiral spring results in an increase of the area moment of inertia by a factor of 4 while the mass remains constant. By reducing the average height, a stabilization of the oscillation behavior of the spiral spring can be achieved in many cases, without the stabilization area having to be provided with an additional mass. This prevents the spiral spring from reaching its maximum oscillation amplitude at a later time due to the increased inertia caused by the additional mass. For putting in addition, both caused by an increase in mass higher friction in the bearings of the coil spring as well as caused by an additionally provided mass imbalance of the coil spring is avoided. It should be understood, however, that 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. - -

The term "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. Since the improvement in the vibration behavior resulting from the present invention also sets in these cases, as long as only the average height of the spiral spring in its stabilization region is at least 1% lower than the average height in the vibration region, then the "average height" or "average height" defined above is determined "Average width" turned off.

As already described above, the total spring length is composed of the inner vibration region and the outer stabilization region. In the following, the delineation of the two areas "inner vibration range" and "outer stabilization range" shall be clarified. 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. In the case of constant heights h _s t and h _sc and constant widths b _st and b _sc , 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. In the case of varying heights h _st and h _sc and varying widths b _st and b _sc , the boundary between stabilization area and oscillation area can be determined by the person skilled in the art with the aid of simple measurements. After determining the height and the width of the spiral spring in defined length sections over the entire spring length, 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". Thus, although the boundary between "inner oscillation range" and "outer stabilization range" is not immediately apparent when a particular coil spring is inspected, For example, 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. Analogously, in connection with the preferred embodiments described in more detail below, 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. - -

Preferably, 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. Particularly preferably, 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. Particularly preferably, 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.

With a change in the cross-sectional geometry of the coil spring in the stabilization region by reducing the height while increasing the width of an increasing increase of the area moment of inertia and an increasingly stable oscillation behavior of the coil spring is achieved. By simply rotating the rectangular cross-sectional area of a conventional spiral spring by 90 °, an increase of the area moment of inertia and a concomitant stabilization of the oscillatory behavior of the spiral spring is achieved without changing the mass.

According to a further preferred embodiment of the present invention, the spiral spring has a constant height h _sc in the inner oscillation range. Particularly preferably, 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. Preferably, 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. Particularly preferably, the coil spring in the externa ßeren stabilization region has an average width - -

b _st , which is at least 12% or 14% or 16% or 18% or 20% or 22% or 24% or 25% greater than the average width b _sc in the inner oscillation range. Particularly preferably, 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. As is known, 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.

Alternatively, however, it is also possible to use a spiral spring which manages without additional mass in the stabilization region. For example, 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.

According to a further realization on which the invention is based, 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 following considerations, which deal with the measures to stabilize the vibrational behavior of the coil spring and its basics, assume that the coil spring consists of an inner oscillation area and an outer stabilization area in which the height - -

reduced and optionally the width are increased. 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.

Basic geometry of the spiral spring The slope of the loop geometry can be of any functional connection. To describe the method, a helical spring with a linear pitch is used by way of example. Also, 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:

Hss) ^■ ■ = rö + / {&) For a linear pitch of the spiral spring:

r (d) == r0 + - · θ

2 × π

Here are:

rO = radius at the point (9 = 0)

P = pitch factor of the spiral spring - -

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.

The associated reference spring to the coil spring is clearly defined by the material used, the initial radius rO, the initial geometry at the point 9 = 0 and the active length of the spiral LE, and the final angle value 9E. to

Simplified, the 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.

Basically, the parameter values are determined so that the respective physical size of the stabilization range from LA (9A) to LE (9E) into

Relative to the vibration range from 0 to LA (9A) is set. This quotient Q1 of the coil spring is then set in relation to a corresponding quotient Q2 of a reference coil spring. The reference coil spring is a spring that - -

at the same number of turns and spring length LE has a winding cross-section which corresponds to the winding cross-section of the oscillation region of the coil spring, ie corresponds in shape and number of turns of the coil spring, but without formation of the stabilization region by reducing the height of the spring. 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.

Stabilization factor r | FT

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).

In order to achieve optimum stabilization of the oscillatory behavior of the coil spring, the stabilization factor r) FT is chosen to be in the range 10 <r) FT <65. - -

Stabilization factor n.k

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:

" ^■ stablejüA - $ E)

kSchwing {0 - M) sprial

here are k _stabi | the spring constant of the stabilizing area of the spiral spring, ksc _h wing the spring constant of the oscillation range of the spiral spring and k the spring constant of the reference coil spring.

In order to achieve optimum stabilization of the oscillatory behavior of the spiral spring 4, 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.

According to a preferred embodiment of the present invention, therefore, 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 (nFT) 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 (nFT) 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

wherein 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, wherein 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 - -

stable (M - üE)

"Swing - M) Spriale

Reference spiral where k _stabi | the spring constant of the spiral spring stabilizing area, k _Sch win _g the spring constant of the oscillation range of the coil spring and k are the spring constant of the reference coil spring, wherein the setpoint range associated with the Fedkonstantestabilisierungsfaktor (r) k) is between 1, 5 and 65, wherein the reference coil spring is a spring which corresponds in terms of geometric shape, number of turns, winding cross-section and spring length (LE) of the coil spring, but the average height h _{sc of} the reference coil spring equal to their average height h _st and the average width b _{sc of} the reference coil spring is equal to their average width b _st .

According to a further preferred embodiment of the present invention, it is at the outer spring support point to a fixed Ansteckpunkt or it is the externa ßere spring holding point formed by a back.

In combination with all embodiments of the present invention, 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 ° , According to further preferred embodiments, 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 ° , As already explained, 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. Preferably, the externa ßere spring holding point is after setting fixed Ansteckpunkt. Particularly preferably, the outer spring holding point is adjusted with a Rücker.

Brief description of the drawings

The invention will be explained in more detail with reference to embodiments in conjunction with the drawings. Show it

1 shows by way of example a perspective view of a vibration system for mechanical watches,

By way of example only, 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

Components of the vibration system according to Figures 1 and 2.

Fig. 4 in an individual representation and in plan view of an inventive

Spiral spring with fixed spring stop;

Fig. 5 in an individual representation and in plan view of an inventive

Spiral spring with back. - -

Ways to carry out the invention

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 ßenseite forms a positive connection with the hub portion 2.3 of the flywheel. Thus, the flywheel is rotatably connected to the balance shaft 3. In addition, 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. In FIGS. 1 and 2, 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. For this purpose, the balance shaft 3 a for receiving the inner - -

Spiral spring mounting portion 4.1 formed shaft portion 3 ", which is arranged above the flywheel 2 receiving shaft portion 3 '., With respect to the balance shaft 3 rotationally fixed attachment of the outer Spirfederfederendabschnittes 4.2, the holding assembly 5 is provided for adjusting the center of the coil spring 4. Die Haltearordnung 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

6.2, wherein 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. By means of the screw 8, which through the elongated guide recess

6.3 of the support arm 6 is guided, 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.

On the opposite lower end face 7.12 of the main body 7.1 of the holding element 7 is a perpendicular to the longitudinal axis LHE of the main body 7.1 extending and downwardly open guide recess 7.3 is provided - -

to the radially leading receiving the externa ßeren Spiralfederendabschnittes 4.2 is formed. 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.

In the assembled state is thus by means of the holding assembly 5 of the radial distance A between the axis UA of the balance shaft 3 and the longitudinal axis LHE of the holding element 7 and thus the outer Spiralfederendabschnittes 4.2 adjustable. By a corresponding radial to the axis UA directed displacement of the holding element 7 and thus the outer Spiralfederendabschnittes 4.2, the coil spring center is adjustable, and preferably such that the Spiralfederringabschnitte 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. In the illustrated embodiment, the externa ßere stabilization region LS is in the region of the outer winding and extends over an angular range α 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. By the in the - -

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, including the stabilization region, 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. For this purpose, 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.

It has already been mentioned above that the spiral spring 4 is made of silicon in a masking-etching process. In order to achieve the required strength and temperature independence, it is advantageous to provide the coil spring 4 or a blank forming this spring on the surfaces by thermal treatment with a silicon oxide layer. The production method (eg masking-etching method) results in not insignificant tolerances of the shape of the spiral spring 4. In order nevertheless to achieve a favorable ratio of stabilization range to oscillation range for the behavior of the spiral spring 4 in the oscillating system, the spring stop point is positioned in the stabilization region, that an optimal vibration behavior is achieved. With the adjustment of the aspect ratio of stabilization range to vibration range and negative influences on the vibration behavior of the vibration system are eliminated, resulting from tolerances of the spring or drive force of a example housed in a spring housing drive spring, in particular also such a drive spring, which increases the spring force - -

or for extending the transition time, for example with diamond coated. Furthermore, by adjusting 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.

In connection with the embodiment shown in FIG. 4, it was assumed that a spring-holding point 13 would be fixed after setting. As shown in Figure 5 but there is also the possibility of using a so-called Rückers 15, which is essentially formed by a pivotable about the axis of the balance shaft 3 lever 16. At the outer end, 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. At its outer end 4.4, the coil spring 4 is connected at 18 fixed to a circuit board or a bearing plate.

The receptacle 17 of the Rückers 15 forms a solid spring support point. By adjusting the back 15, 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. In the illustrated embodiment, the stabilization region LS extends over an angle α 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 Rücker 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.

LIST OF REFERENCE NUMBERS

1 oscillating system or balance

2 swinging bodies

2.1 outer circular ring section

2.2 spokes

2.3 Hub section

2.4 flywheel

3 balance wheel

3 ', 3 "shaft sections

3.1 upper free end

3.2 lower free end

4 spiral spring

4.1 coil spring attachment section

4.3 Spiral spring ring sections

4.4 outer spring end

5 holding arrangement

6 holding arm

6.1 inner retaining arm

6.2 outer retaining arm end

6.3 elongated guide recess

7 holding element

7.1 basic body

7.1 1 upper end side

7.12 lower end 7.2 blind hole

7.3 guide recess

8 screw

9 turn

1 1 .1 - 1 1 .4 sections of stabilization area LS

12 inner end of the oscillation range

13 Spring holding point

14 spiral spring length

15 back

16 levers

17 recording

18 attachment

UA axis of the balance wave

A radial distance

LHA longitudinal axis of the lever arm

LHE longitudinal axis of the lever element

α angular extent of the stabilization area LS

LA vibration range

LS stabilization area

Claims

claims

Oscillation system for mechanical movements comprising a vibrating body (2), about a shaft (UA) pivotally mounted balance shaft (3) and a coil spring (4) with a total spring length, wherein the total spring length of an inner vibration region with a vibration spring length (LA) and a outer stabilization area with a stabilizing spring length (LS) composed,

wherein the coil spring (4) is connected to the balance shaft (3) by a coil spring attachment portion (4.1) enclosing the balance shaft (3), the coil spring (4) being held or clamped in the outer stabilization region at a spring retention point (13),

wherein the total spring length extends from an inner end (12) of the inner vibration section to the outer spring support point (13), wherein the spiral spring (4) in its inner oscillation area parallel to the axis of the coil spring coincident with the axis (UA) of the balance shaft average height h _sc and has an average width b _sc radial to the axis of the coil spring,

characterized in that the spiral spring (4) in the outer stabilization region parallel to the axis of the coil spring has an average height hst which is at least 1% less than the average height h _sc in the inner vibration region and

in that the spiral spring (4) has an average width b _st in the outer stabilization region radial to the axis of the spiral spring which is at least 1% greater than the average width b _sc in the inner oscillation region.

Oscillating system according to claim 1, characterized in that the spiral spring (4) in the externa ßeren stabilization region has an average height h _st , which is at least 10% less than the average height h _sc in the inner vibration range.

Oscillating system according to claim 1 or 2, characterized in that the spiral spring (4) in the externa ßeren stabilization region an average height hst, which is at least 25% less than the average height h _sc in the inner vibration range.

4. oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) in the outer stabilization region has an average height h _s , which is at least 50% less than the average height h _sc in the inner vibration region.

5. oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) throughout the inner

Vibration range has a constant height h _sc .

6. oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) in the entire outer stabilization region has a constant height h _s .

7. oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) in the outer stabilization region radially to the axis of the coil spring has an average width b _st , which is at least 10% larger than the average width b _sc in the interior

Vibration region.

8. oscillating system according to claim 7, characterized in that the spiral spring (4) in the outer stabilization region has an average width which is at least 20% larger than the average width b _sc in the inner vibration region.

9. oscillating system according to claim 7 or 8, characterized in that the spiral spring (4) in the outer stabilization region has an average width bst, which is at least 30% larger than the average width b _sc in the inner vibration region.

10. oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) in the outer stabilization region has an average width b _st which is at least 50% larger than the average width b _sc in the inner vibration region.

Oscillation system according to one of the preceding claims, characterized

characterized in that 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 their outer stabilization region are coordinated such that a second moment of inertia (r) FT) one in a the moment of inertia stabilization factor (r) FT) having a predetermined setpoint value range associated therewith and / or a Fedkonstantestabilisierungsfaktor (r) k) in a the Federkststestestisierungsfaktor (r) k) associated predetermined setpoint range lying value, wherein the second moment of inertia stabilization factor (r) FT) by the ratio of a first quotient represents a second quotient, wherein the first quotient of the ratio of the moment of inertia of the externa ßeren stabilization region of the coil spring (4) to the area moment of inertia of the inner vibration region of the coil spring (4) and the second quotient is the ratio of the area moment of inertia of a spring length corresponding to the stabilization area to the area moment of inertia of a spring length of a reference spiral spring corresponding to the oscillation area, in accordance with the formula

where FT (I) is the course of the area moment of inertia of the spiral spring (4) as a function of the spring length (I) and FTn (l) is the profile of the area moment of inertia of the reference spring as a function of the spring length (I),

wherein the setpoint range associated with the moment of inertia (R) FT) is between 10 and 65, the spring constant stabilizing factor (r) k) being the ratio of a first quotient to a second quotient, the first quotient being the ratio of the spring constant of the outer stabilizing region the coil spring (4) to the spring constant of the inner vibration region of the coil spring (4) and the second quotient the ratio of the spring constant 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 stable (M - üE)

"Swing - M) Spriale

Reference spiral where k _stabi | the spring constant of the stabilizing area of the coil spring (4), ksc _h wing is the spring constant of the oscillation area of the coil spring (4), and k is the spring constant of the reference coil spring,

the setpoint range associated with the spring constant stabilizing factor (r) k) being between 1.5 and 65, the reference coil spring being a spring which corresponds in terms of geometric shape, number of turns, turns and total spring length of the coil spring (4) but the average height h _sc the reference coil spring is equal to its average height h _st and the average width b _{sc of} the reference coil spring is equal to its average width b _st .

12. Oscillating system according to one of the preceding claims, characterized in that it is at the externa ßeren spring holding point (13) is a fixed Ansteckpunkt or externa ßere spring holding point (13) by a back (15) is formed.

13. Oscillation system according to one of the preceding claims, characterized in that the stabilization region extends over an angular range between 30 ° and 100 ⁰ .

14. Oscillating system according to one of the preceding claims, characterized in that the spiral spring (4) made of a non-metallic material, preferably made of diamond or of silicon with a coating of silicon oxide.

15. Mechanical watch with a mechanical oscillating system, characterized in that the oscillating system is designed according to one of the preceding claims.

A method of adjusting a vibratory system for mechanical movements according to claims 1 to 14, comprising the step of adjusting the total spring length by changing the outer spring holding point (13).

A method according to claim 16, characterized in that the outer spring holding point is after setting fixed Ansteckpunkt (13).

18. The method according to any one of claims 16 or 17, characterized in that the externa ßere spring-holding point (13) by a Rücker (15) is formed.