DE1763351C - Electromechanical resonance motor with swing arm held on one side - Google Patents

Description

according to claim 3. d ^ ch '^ veHäss,

KSSS "

The solution is given below with the help of Drawings on the basis of examples

"Ic.-Rnnduneboeh" on an elect ^ mechan, - "0 closer crl5u, cr .. ^^ f ^ S.f ^ ans.ch, ÄÄr ei 'ers ^ execution form of the "Hndun ^ Oen

u, f Hicgung in one direction elastic and in to * ψ ™ ^η ζ ™haben ^. _gcsdinll , ene view on the

Jicscr vertical direction rigid on one side gchal- Mg- <lic n-iiwus y

, cnen swing arm and one at the free end of the swing arm- * 5 ^ ™ "™« ^ ™ _c ^ hniUene side view of a

ÄT ^! ^ R "-A ^b Dre ^ cS ^ W ^ rm of the invention.

around a virtual oscillating axis Mi.sführi. on- RcoiKin / molors.

63

pig
,: _ner dr ^:
Resona;

one vk

Resona:

pig.

Resona
pjn

form ^
two S.

hr.u

the partially gc

■ embodiment dc

rotors,
the partially atonement

-τ embodiment d ·.

-; o ^ rs.

j; e partially schnu
-nor according to Fig. 5.

., nd 8 views one
.. "according to the invention

'■

broom
arms
pi

üid 10 Schemaski /. - \ η
.nd a resonator.
Resonance motor /; n

and 12 the bill. ;;
ngarrns of an Rcm · !.

Deflection at ποπ

"'"■'""'^ ⁱ '" ^u "'""·''■' ■ ■
-Uing of the held

the, ii

rende '·

best ;!

meclK.

Green

the German
slim
the SC
to '■
sen V r
leaves
Spall:

the schematic _Γ>; : -. :: '!.;ιΐ;:;;: · .-. ..>.

r in a lindun ^ ovvd'ce. i!: m, _{m; i} « _; .

Application komiru · '-, -. · ■; , 'hei r ..--; i !! focus of the Mv. en- ¹ .- ^1. ! ■., -! / Or half of the swing axis lies.

ι g. 1 and 2 show an f-U: Mir.an, Mv, .. ior.

■, .special together with cu ^ -r · ■ v> nchror.:sieiangfolder. for electric wristwatches is. It essentially has an electrical power Energy converter, a Rcsonaii> r and , .en ratchet gear mechanism on and lsi on one latte I arranged.

• '"sonator has.-White weights 2 and *, Always connect a stiff arm 4 to one another. Weight 2 is active in the sense that

30th

uis a magnet with / white / ui maiider <.; ui image plate 1 parallel I laugh and ai da / u! iten permanent magnetization is formed. Es Ii parallel to the base plate opposite an O ₁ Ju.,. move an electromagnet 6, the \ on in two coils 7 and 8 from is excited. The weight 3 is used; il · - counterweight to the magnet. A suspension of the weights 2 and 3 and the stiff Anns 4 consists essentially of oscillating arms 9 and 10 running approximately parallel to the base plate I, on which thinned areas II and 12 are elastic in bending. One ends of the swing arms 9 and! O are clamped to a fastening piece 13, which in turn is fastened to the base plate 1 of the watch. Located on the stiff arm 4; There is also a pin 14. At the outer end of the pin 14 there is a very fine, resilient lamella 15 which carries a latch block 16 and extends essentially parallel to the rigid arm 4. The lamella 15 forms /.together with the ratchet 16 ″ ine drive, y. klinki, which drives a ratchet wheel 17. This · - Shahraii has a large number of teeth on the umlaiij '. A llalteklinke 18 clears the movement of the sonic wheel 17 the same and veihmderi. that this is about: -incn tooth or more backwards ·. turns. The ^Halle-ri jack 18 is befestig to a post l ^l> !. The Ui-sonan / nioior works as follows:

Under the action of \ "n forces at <. \ Cn free ends of the Schsvingarmc 9 and IO, the thinned, elastic areas II and 12 are deformed approximately cranially. The free ends of the Schwisigarmc 9 and 10 move approximately on circular paths, The center points of the circular paths lie on a virtual oscillation axis, the position of which is indicated by a dash-dotted line 20. The masses of weights 2 and 3 of the rigid arm 4 are distributed so that the common center of mass There are thus equilibrium conditions with respect to the mass system in the area of the oscillating axis 20. The normal oscillating movements of the mass system are therefore practically rotational movements about the virtual oscillating axis 20.

However, the deformation of the elastic, thinned areas 11 and 12 of the oscillating arms is different when the post 13 and the held fins of the oscillating arms are accelerated from that under normal oscillating movements of the resonator. A shock on the post 13 and thus on the held enders: the two swing arms 9 and 10 perpendicular to their main direction have an S-shaped deformation of the elastic areas U and 12 as a result, since the weights 2 and 3 as well? move the rigid arm 4 relative to the post and the base plate 1 under the acceleration without a rotational movement parallel to itself. One : S-shaped deformation oppose the elastic, thinned areas 12 and 12 of the two oscillating arms so much higher resistance than a bending in the same direction that the parallel deflection of the mass system under the action of impacts is relatively small.

According to E i g. 2 of the drawings is lamella 15 of the drive pawl aligned approximately parallel to the resilient, thinned areas 11 and 12, i. perpendicular to the direction of least resistance to deflections that occur when the Base plate 1, the post 13 and the held ends of the swing arms 9 and 10 can occur. Therefore practically changes with an acceleration in the mentioned direction of the lowest resistance the distance between the holding pawl and the pawl block 16 of the drive pawl is not. A shock or an acceleration parallel to the lamella 15 of the drive pawl produces practically no mass displacement and deformation, since the clasti see thinned areas II and 12 are very stiff in this direction. Only pure ones step in this direction Tensile or compressive forces. Just a relative movement of the pawl 16 parallel to the lamella and to the wing arms 9 and 10 under the Ein-ΠiiIi a jolt could produce a counting error on ratchet wheel 17. Such a counting error occurs biMin resonance motor according to the invention does not occur. The desired resonance frequency can be set on the counterweight 3. This counterweight is > Min one axis 21 rotatably arranged and has a Flat 23 on. so there * the focus outside the axis 21 lies !. When turning, the counterweight 3 the center of gravity is shifted along the rigid arm 4, line safety screw 22 holds the counterweight 3 in its L.age. The resonance frequency is set by shifting the mass on the counterweight dynamic equilibrium of the mass system against Shin, however, is only insignificant

Equilibrium of the mass system over the swing arms but only insignificant

65 influenced.

In the Ai'.sleituugsform des Resonan / m according to E i g. 3 of the drawings are opposite to the resonance motor according to the two E i g 1 and 2

riiors

g 1 and 2 nui

Function and location of Schwingann and stiff Arm swapped. The resonance motor according to FIG. 3 is in turn built on the base plate 1 and has a resonator with two weights 2 and 3, which are connected to each other via a rigid arm 4 in Vcr-S commitment. The stiff arm forks into two arms 29 and 30 which embrace a central opening. The weight 2 is a permanent magnet and can be positioned opposite a gap 5 of an electromagnet 6 shift. The electromagnet 6 has two coils 7, only one of which is shown in FIG. 3 of the drawings is visible.

The mass system consisting of the weights 2 and 3 and the rigid arm 4 is on one Swing arm 9 'suspended, which has an elastic, thinned area 1Γ on bending. A fastening piece 13, which is attached to the circuit board 1, holds the swing arm 9 '. Located on the rigid arm 4 a pin 14, at the outer end of which a resilient lamella 15 is attached. At the front end of the Lamella there is a ratchet block 16 which, together with the lamella, forms a drive pawl. The drive pawl drives a ratchet wheel 17, the movement of which is rectified by a holding pawl 18 will. The retaining pawl 18 is firmly connected to the base plate 1 via a post 19. The function of the resonance motor according to FIG. 3 corresponds to the function of the motor according to FIGS. 1 and 2

The resonance motor according to FIG. 4 of the drawings differs essentially from that according to 3 F i g. 3 only in that the stiff arm does not fork into two arms in the central area. According to the illustration in FIG. 4, the resonance motor is built on a base plate 1. The resonator has two weights 2 and 3 which are connected to one another via a rigid arm 4. the with the reference number 29 marked middle part of the rigid arm 4 towers above other components of the resonance motor. The weight 2 consists of one Magnet, which is exposed to a gap 5 in the otherwise closed yoke of an electromagnet 6 can move. The electromagnet carries two coils 7, from which only the one in FIG. 4 is visible.

The mass system formed from the weights 2 and 3 and the rigid arm 4 is in its central region suspended from a swing arm 9 'which has a thinned area 11' which is elastic in terms of bending. The swing arm 9 'is clamped at one end to a fastening piece 13 and stands with the Base plate 1 in a fixed connection. On the arm 4 there is a pin 14 which has a resilient lamella 15 wearing. At the outer end of the lamella 15 there is a ratchet 16, which together with the lamella forms a drive pawl. This drive pawl is approximately parallel to the swing arm 9 and to the stiff Arm 4 aligned. The pawl drives a ratchet wheel during normal oscillation movements of the resonator 17, the movement of which is rectified by a retaining clip 18. The Halleklinkc is above one Post 19 with the base plate J in a fixed connection. Also the function of the resonance motor F i g. 4 corresponds to the function of the motor according to FIGS. 1 and 2.

The resonance motor according to FIGS. 5 and 6 has an electrodynamic energy converter and is built on a (5round plate 1. Two horseshoe-shaped Permanent magnets 66 and 67 of the electrodynamic energy converter generate two magnetic fields, which are each indicated with a circle and the two reference numbers 68 and 69. The magnetic fields are approximately perpendicular / ur base plate 1 and are opposite to each other.

The horseshoe-shaped permanent magnet 66 is composed of two magnetic plates 72 facing each other directed poles and particularly high magnetization and made of a U-shaped soft iron yoke 74 together. The permanent magnet 67 also has two magnetic plates 73, one of which, however only one in Fig. 6 is shown. In the case of the permanent magnet 67, too, the two magnetic plates 73 are through a U-shaped yoke 74 connected to one another.

Between the polar magnetic plates of the two permanent magnets 66 and 67 there is a coil 75 on one movable carrier 78 is arranged, which in turn is clamped between two fastening plates 79 and 80 is. Screws 81 and 82 together with electrically insulating nuts 8Γ and 82 'form the Connection between the mounting plates 79 and 80. The electrically insulating nuts are in corresponding Depressions in the lower mounting plate 80 are used. In Fig. 5 of the drawings an electrically insulating nut 82 'which is inserted into the corresponding depression 82 ". The mounting plates 79 and 80, the screws 81 and 82 and the nuts 8Γ and 82 'together form a Counterweight to coil 75 in the entire mass system. Via the carrier 78 and the mounting plates 79 and 80 the electrical power supply / air movable coil 75 takes place.

The two fastening plates 79 and 80 are in turn elastic in each case by a flexure Swing arm held. The two swing arms are identified by the reference numbers 9 and 10. she go at one end into fastening tabs 85 and 86, which in turn are electrically isolated two screws 87 and 88 are connected to the base plate 1. The upper mounting plate 79 carries a resilient lamella 15, at the front end of which a latch end 16 is arranged. The resilient one Lamella 15 together with the ratchet block Ii forms a drive pawl which is at least approximately parallel is aligned with the swing arms 9 and 10. The drive pawl engages the teeth of a ratchet: 17, the movement of which is directed in the same way by a hall latch. The holding clip consists of the Klinkenstein 18 and a resilient lamella 93 which via a post 19 with the base plate ' connected is.

The functioning of the resonance motor according to dei F i g. 5 and 6 corresponds to the function of the motors up to 4 with the only exception that instead of a electromagnetic energy conversion in the embodiment according to FIGS. 5 and 6 the energies is converted electrodynamically.

In the embodiment of the resonance motor according to FIGS. 7 and 8 the conversion takes place from electrical energy into mechanical into a clektrostrictive double lamella of piezoelectric Material. This double lamella must be designed to be relatively long so that it can low electrical voltage makes a sufficiently large movement.

The resonance motor according to FIGS. 7 and 8 v, built on a Grundpiaitc 1. The reference number 96 identifies the trostrictive double camel made of piezoelectric material. The one end di

Double blade is clamped in a holder 97, exceeds a certain value, were relative from the one foot 98 by two screws 87 and 88 movements of greater extent between the mass knob the base plate I is attached. Two line system with weights 2 and 3 and the Giund-101 and 102 are used to supply electrical energy plate 1 occur. With the bumper 116 and the to the double lamella 96. Rclativbcwegiingcn are attached to the free egg of the double cones 118 lamella is a weight 3, which is limited to a particularly large acceleration. the A counterweight 2 is assigned to the rigid arm 4. There is no deflection of the mass system in the case of Stöl.kn On the counterweight 2, a resilient lamella 15 is only limited in order to sort out counting errors on the pawl, to avoid a ratchet-ratchet gear at their outer end, but rather, stone 16 carries. The resilient lamella 15 also prevents damage to the mostly very sensitive ones Together with the latch block 16, a drive latch to prevent double lamellae.

which engages the teeth of a sonic wheel 17. The axis of rotation of the swivel movement in the! "All

Klinkenstein 18 forms together with a resilient acceleration of the base plate perpendicular to the

Slat 93 is a hall latch, the movement of the double slat 96 is parallel to the pivot axis 119

Schallntdcs 17 rectifies, the holding pawl is at i ₅ and cuts the double clamps near the

a post 19 on the foot 98 of the bracket 97 latch plate 106. The position of the axis of rotation

clamped. With an actuator, not shown, the distance between Masscsystemv: rk-

lälil the contact pressure of the retaining pawls on the puncture and double lamellcnmiltc is determined. Here but

Set the teeth of the ratchet wheel 17. this distance is freely selectable, is also the position

The weight 3 has a screw 112, the 20 of which can freely select the axis of rotation, so that

inner end presses against a clamping disk 113. you can easily lay them in such a way that they the

The ratchet lamella 106 is cut with the screw and the clamping washer.

Weight held on the double clamp 9. The other in the Atisführungformen according to the invention

The end of the double lamella 96 is in the holder 97, FIGS. 1 to 6 guarantee the following properties

clamped with the help of a screw 114, 25 of which are unequivocally relative to the Rcsonan / motor

inner end presses against a clamping disc 115. Bump:

Both clamping washers !! 113 and 115 are on the _{a) D. 1S Masscnsystcm slent in} equilibrium in

same I-pool of the double lamellas 96 aiii. _{bc7llg to dic v} i _rUlc || _c swing axis;

The rigid arm 4 carries a bumper 116, in _h) <] _{cr an} elastically flexible area of the swing arm

which is an elongated hole 117. In this long 30 _dcs resonator is relatively short;

Hole protrudes a pin 118, the aiii of the base plate I _{c) dic} Anlricbsklinkc of the pawl sound wheel Gc-

is required. tricbes is roughly parallel with one thrust

The resonance motor in the embodiment according _{to the} swing arm of the resonator aligned, the F i g. 7 and 8 works like this:

The double clamp 96 serves as a mechanical 35 in the embodiment of the invention Energy converter and at the same time as a swing arm of the according to the F i g. 7 and 8 stand the mass system in Resonator, to which the weights 3 and 2 as well as the relation to the virtual oscillation axis are not in the same way Arm 4 as an essential part of the Schwinweight. But this is what the lamella of the drive mechanism stands for Are assigned to the mass system. The normal jack in the direction of its thrust perpendicular to one Schwingiingsbcwcgung is a rotational movement of the 40 axis of rotation around which the mass system in Bc mass systems around a virtual oscillating axis that rotates at a slow pace. There is also in ! i g. 7 by the dash-dotted line 20 a η ge the latch block 16 of the drive latch and the impact is. With normal Schwingungsbcwegung falls point of the pawl on the ratchet 17 very close to this the pivot axis 20 with the axis of the pin 118 axis of rotation.

together. The width of the elongated hole 117 in the joint 45 In the embodiments of the crlindiingsgcn

Catcher 116 is larger by a certain amount than the resonance motor according to FIGS. 1 to 6 is the

the diameter of the pin 118, so that with a normal axis of rotation around which the mass system at acceleration

Oscillation movements of the pegs the inner walls movement executes a pivoting movement at infinity

of the elongated hole 117 is not touched. The resilient lamella on a level in which the swing arm in the un-

15 of the drive latch is perpendicular to the Doppcllamclle 5 ° excited state of the resonator. Therefore must

96 aligned, and in a sufficiently large also the drive pawl approximately parallel to the respective

Distance from the swing axis 20 that be aligned with normal swing arm.

Oscillation movement of the mass system of the Reso- With the help of F i g. 9 to 13 can be traced back to the theory

nanzmotor derive the shock movement of the drive pawl of the resonance motor according to the invention,

on ratchet 17 is large enough. 55

When the base plate 1 accelerates, case a (FIG. 9) the weights 3 and 2 and with these the whole,

A mass system suspended from the double lamella 96 A point-shaped mass (s), vibrates on one deflected relative to the base plate 1 and experience cantilevered swing arm, which is close to the a rotational movement, the axis of rotation of which is short, elastic to bending Togen on the base plate 1 in FIG. 8 has the drawing area. The funding conslant in this term, runs perpendicular to the plane of the sheet. Both rich is denoted by A (torque, related the lamella 15 as well as the double lamella 96 cut to the unit of the angular displacement of the mass). this axis of rotation is essentially perpendicular. The Dic mass carries sinusoidal oscillations Lamella 15 is thus at an acceleration of 65 with a movement on an arc of a circle Base plate 1 in the direction of impact of the drive latch center point, which is exactly in the middle of the elastic Practically not notched in relation to the base plate. Range. The distance between the mass ifs a shock or other acceleration a center of gravity and the center point is 1, loading

ίο

draws. The circular frequencies /. <n, the natural oscillation can go through

/ '4 μIf, Q
'", 0.04 gr.

200;

2τι ■ 30011 /,

k / Y A /// ;,

(D This becomes

be expressed.

./ means the moment of inertia of the mass with reference to the center point as rotation / .cn-Irum.

If the clamping point of an acceleration « in the upward direction, the middle position of the mass with reference to the clamping point, shifted downwards as shown. The lungs of the Shift is denoted by / i ". It amounts to

Zi _n '»ι 1" f <- // A. (2)

If the angular frequency is introduced into formula 2, the length /; ,,

ha fl / f '/ f (3)

134 m / sec ² 13.7 χ

The specified permissible accelerations are usually greater than those that are usually used human arm occur. With certain

Activities, however, the peak values of the laic accelerations are considerably higher than the calculated maximum permissible accelerations. Seen from the formula 6 according to that one can increase the z.iilässige acceleration, and thus the safe healing for accurate time display of watches, in one liem öcn energy consumption and reduces the Qualilätsfakior or Zählfrequcnz erhöhl or the mass of the resonaten Schwingsysteins. Other loading

From formula 3 it can be seen that a fixed 20 conditions prevent the mentioned

Relationship between the natural frequency, a rcsonan- size can be changed significantly, th system and the deformation, which is under ways to increase the security of the influence of an acceleration on the rcsonant display are very small because you System occurs. The function between deformation differed for this in decisive quantities in FOi and natural frequency is independent of the type of 15 under a root.

The il-

elastic suspension.

In the following, the amplitude of the vibratory movement of the masses is denoted by A, the power output during the vibratory motion by P and the quality factor of the system including the ratchet and ratchet gear is denoted by Q. The functional relationship between these variables is known (Horological journal, March to July 1963, pp. 81 to 233), namely:

FaIIb (Fig. 10 to 12) resonator with excluded Mass distribution in a balanced mass system

A -

2PQ

(4)

W ₁

10 shows the simplified scheme of the resonators in the motors according to FIGS. 1 to 6. A mass in, is in equilibrium with a mass / n ₂ with respect to a region of a swing arm that is elastic here. The Si I 35 arm is clamped on one side and at the end holds the M. system consisting of the two masses. The mass of a stiff arm that supports the! Masses i? J, and m ₂ connecting, will be vcrnachl. On the other hand, with the correct setting, the balance / between the two masses should lie! The pawl opposite the ratchet wheel has the amplitude of 40 if the following conditions are met: Drive pawl equal to the length of the teeth on the 1st. The center C of the flexurally elastic B «

Be sonic wheel. The permissible deviation of the drive pawl from the middle position is half Limited to the length of a tooth. This results in 'lic condition

ha < ^A . (5)

When equations 3 and 4 are introduced into Formula 5, it becomes

is on the straight line that connects the mass points of the two masses m _t and i? i ₂ ! 2. The distance between the masses. point of the mass m, and the center C at the distance L between the mass vertical · ■ '■ mass; n _s and the center C of the elastic region;: area must satisfy the function:

/ n, /, - W ₂ I ₂ .

a <

ι /

PQw ₁ 2 in, So there is equilibrium when the Ma (6) center of gravity of the whole on the swing arm; n

hung mass syslems on the virtual ScIiv. The axis is due to the flexural elasticity> The permissible acceleration at a tuning fork area of the swing arm and its center clock, where the gear folder is made up of two parallel ones. mutually oscillating resonators
F i g. 9 can be calculated as follows, for example:

P =: 4.5 μ W, Q = 1640, w, = 2π ■ 360 Hz, im, = 0.565 gr.
So that will

a <121 m / sec ² = 12.4 g.

Here, g means the acceleration due to gravity. Different resonance motors of electronic wristwatches show the following values:

According to the illustration in Fig. 11 of the drawing ^! gen deforms the lamella, which represents the flexible elastic area of the swing arm. βο normal oscillation movement circular. resonant angular frequency o>, this oscillation movement is given by:

using equation (7) then follows

With an acceleration of the fin clamping point vertically deformed into a clamped lamella, which represents the elastic area of the swing arm in terms of bending the lamella is in a different way, and / was approximately as shown in FIG. 12 of the drawings. With perfect equilibrium, the lamella assumes an S-shape and the tangents to the luden of the lamella run parallel to each other. The freely displayed mass system is therefore opposite to the Clamping point deflected parallel to itself, and / was by the following amount

/ '- 4 μ IC, Q 200, ι ,, 2;
zn Im ₁ 0.08 gr.

4.5 mm, L ₁ - 1, H mm, r _r

300 Hz.

1.8 mm

2910 m / sec- 295 j?

(/ 7I ₁ I / H ₂ ) II «/ 12 λ.

(10)

Expediently, the amount of deflection comes as a function of one's own Krcisfrequenzw ,; to expression, which is assigned to the direction of acceleration

ha ■■ - ajiii'- ,. (11)

Fine angular frequency W ₁ is assigned to the direction perpendicular to the plane of the lamella.

«> .Jm, 3.464 r, //;,. (12)

Thus, with r “the turning radius is designated, which determines is through

(13)

r _g * Jim

nu).

The imperviousness to accelerations the clamping point can therefore be reduced by a factor of 24 in the last-described case compared to case a improve.

In the first four described embodiments according to FIG. 1 to 6 of the resonance motor according to the invention, the drive pawl is aligned parallel to the swing arm or to its flexurally elastic region. Accordingly, an acceleration at the clamping point of the swing arm perpendicular to this does not result in a phase shift of the drive pawl relative to the holding pawl and the ratchet wheel, but only a certain change in the pressure of the drive pawl on the tooth flanks of the ratchet wheel. Only an acceleration in the direction of impact of the drive pawl could theoretically cause a deflection of the drive pawl in the direction of impact with respect to the clamping point. The own angular frequency (U ₃ , which is assigned to a corresponding deformation, is

hi denotes the total mass of the on the swing arm freely suspended, swinging mass star.

If a drive pawl is arranged on the flexurally elastic lamella and perpendicular to the Lamella is aligned, it is both by the normal, resonant vibrational movements as even when the clamping point is accelerated, it is dislodged in the direction of impact. At a S-shaped deformation of the lamella of the swing arm are the elastic counter-forces in the lamella however, it is far larger than the normal, circular arc-shaped one Deformation. The deflection of the drive pawl in the direction of impact is therefore below the The influence of accelerations is relatively small and the maximum permissible acceleration is higher than in case a. The amplitude can be used for the. Case b using the following formula, which replaces equation (4)

"hl"

3.464 r _g each.

Here, c is the thickness of the flexurally elastic lamella of the swing arm. Since e>_;!ru,;, the maximum permissible acceleration taking into account formula 14 is given by

\ 2r _tJ r _c
e ²

2 / H

(16)

lPQ

45

a <

(14)

Here r _{c means} the distance between the drive pawl and the virtual oscillating axis. In Fig. 10, the point P indicates the position of the drive pawl. so If you put equations 4 'and 11 in formula 5, we get

XJPQm ₁

^r

The maximum permissible acceleration can therefore be increased considerably if one lets iuj ^ - ω become. In case b, ω _α = w ₂ . Using equation (12) it follows :

6o

\ 2r _e r _c λ! PQm ₁ ^{a <} "~ H""| / im"' For example, if r 4.5 mm, e --- 0.1 mm, the factor by which the square root must be multiplied is 7800. This factor is so large that an impact on the clamping point parallel to the impact direction of the drive pawl has practically no influence on the deflection of this drive pawl. Such a shock cannot lead to a counting error.

Case c (Fig. 13) Resonator with unbalanced mass distribution in the freely suspended mass system

Fig. 13 represents in a greatly exaggerated form the position of a mass system with masses distributed over a large area, a lamellar, elastic on bending Swing arm, which holds the mass system at one end, and a clamping point at the other The end of the swing arm in the state of acceleration at the clamping element in the upward direction The deflection of the free end of the swing arm! amounts to

(15)

If the lamella of the swing arm, which is elastic to bend, is short compared to the radius of rotation of the swing arm, a very substantial increase in the maximum permissible acceleration can be achieved. This ztigt the following sample calculation where E is the modulus of elasticity of the swing arm: and J the moment of inertia of the swing arm cross-section as a constant.

The rotational movement of the free ends of the swing arm is

in a I ₃

II '

₂₁₁

The deflection of a point P in relation to the main axis of inertia in which the vibrating yarn is located

is in the de-excited state of the resonator, is

h _v h-lp-Λ. (19)

From a two-dimensional perspective, there is a point N which does not change its position with respect to the clamping point under the influence of acceleration. Its distance from the free end of the swing arm is given by the condition /; ,, - 0 and can be calculated using the formulas

I ₁₁ U

3A ₁ - big

(20)

(21)

The point λ 'represents in Fig. 13 in three-dimensional Considering an axis of rotation. In the embodiment of the invention

Resonance motor according to the F i g. 7 and 8, the drive pawl is perpendicular to such an axis of rotation aligned. It experiences no deflection in the direction of impact when the clamping point of the swing arm is accelerated perpendicular to the swing arm.

The equilibrium condition can be expressed by I ₉ - I.J2. From this follows I _n = cv>. So when the freely suspended mass system is in equilibrium with respect to the virtual oscillation axis, the axis of rotation is at infinity. This case is the case with the embodiments of the resonance motor according to the invention according to FIGS. 1 to 6 given.

You can use constructive measures to

The axis of rotation, which is indicated by N in FIG. 10, is moved to a point at which the normal oscillation movement has an amplitude that is sufficiently large for the ratchet-sonic wheel gearing. For example, if the Roialionsachse (/ V) should intersect the clamping point, I _n - = A, and Ig ----- / _; , / 3.

1 sheet of drawings

Claims (1)

1. Electromechanical resonance motor for Ein R ^ " ³ " * ™ ¹ ^ 'wrote, which is a portable precision timer, with a 1 atentscnmi. .ι . _{h ine} Masscnverteilunc resonator of the at least one elastic ^ Xi ^ SLtens two "" De "heavy one direction on bending in the 5 and in this perpendicular in ^R a ™ * e rigid _gleicheI1 Schwingmomenlen against right direction, cantilevered P"^"kt!; ™ ¹ ^ * _hse and their total swing arm and one at the free end of the _{swing arm} over the Schwmgac swing axis. This, -arm held mass system that be. Excitation ^^^ "^. ^ Contains a in the Uhrentechn.k where! U of the resonator at least approximately torsional, o Reso ^na _t ^nOT ° ^t ?" _A X " _ad _ _G elriebc for conversion" executes around a virtual oscillation axis, ^heka ^^^ _e ZZ ^ in rectified three, and with an oscillation attached to the resonator; ^BE * ^e - ^U ^ j _^funct ion of a derund cooperating with a ratchet wheel ^ movements Fur J ₁ *, provided that the rotary Aniricbsklinkc, characterized geke π η ζ e, ch - * ''& ^η £ ^Λ ™™ ¹ * ™ _{αυ with} the virtual Schwin, net that the drive pawl (15) is attached to the resonator, 5 axis of the armature exactly _{further emKh} so that the line on which the drive axis coincides, the pawl (15) hits the ratchet wheel (17). _hekann , _e r Kesonanz.nuior the entrance is practiced, the virtual axis of rotation intersects to Another known r _{hrift 39} . ₁₇₄₆ ), b, which the mass system (2, 3, 4) at acceleration f is ^called f ^ ¹ ^^ 'also essentially euv of the held end of the swing arm (4) one, o which the Mu esystem ^ _mJRdesteil . Rotary motion, and that the resonator mass _{ve ^ U ng ni ^ n Schwun} , is designed so that the virtual axis of rotation and two other ^S ^^ ^P ^ "^ oscillation axis are defined virtual swing axis do not coincide ΓΤ? " 2. resonance engine according to claim 1, characterized the GesamÄscin * ^ epu _{ResQmtQT be} ordnoR. marked that the mass system from an * _s axis lies ver ... - - conversion available. stiff arm (4) with both ends being ™ ^ *% ^ £ ^ _{in the} same direction of rotation solid masses (2, 3), the parallel to ^^ '«^' '^^ schwjngarme this resonance _{the one or the one through a fastening piece} (13) a ^ "" ^ "^" S, ctw a parallel to the connection * - each swing arm held or low-9 or ^ "^ Ζ'Ζη two outer areas ,, 9 and 10) extend so attached thereto that 30! .nie zwisc hen Denj ^ e _Trained! t _dc and the center of gravity of the mass system and the and are behaved msm t resonator Schwingach * coincide, and that the occurrence of a shock very Urr J _f ^ ^^ drive pawl (15, 16) to the stiff arm (4) and to is a = W.nke anfeCürd. ^ _Coating , the swing arm or arms (9 'or 9 and 10) exerted SU » ^L " ^cug ' _f - _{hr lcich large} , which is parallel (Fig. 1 to 6). 35 de ^^ "iXS ^ g ^ he insensitivity 3. Resonance motor according to claim 1, characterized in that cmc "^ '^ Λ ^" ^ t becomes. This resonator characterized that the mass system consists of an opposite stobe c ^ _dje " _rucnu " _ stiff arm (4) with at both ends proves j cdoc de η N ^ ^c '^ _{or lamellae} solid masses (2, 3) parallel to gen, the re at.v ku. to ^ cg ^ which by a bracket (97) emsc.lg gchal- 40 seh large ^ smd ^ / 1 V rg ^. ^ _Schwjngarmc , cnen swing arm (96) running on its cracks st cs ^ jr fc resonator again free end with the one at one end; ^{CI 'a} ^ ^in' S, _{Icher, since} a considerable brought mass (3) mounted so as st, in that the other against poking emj _{"a erheblic} he deflection of mass (2) nahederHatterung (97) .. zuhegenkomm Ve fοr ^ ₁ ung and thus e ^ _{5 ResonaU) rs} that the drive pawl (15, 16) in the vicinity of this 45 of the pawls wearü other mass (2) occurs perpendicular to both arms. based on the (4 96) is arranged and that the Schwingann De. F.rhndung l.Lgt c Ai g _Re ^, _nanzmotorcn 96) from an electrostrictive «.. double name as se hard night te.l cd be ^" ^ ^ ^^ electromechanical energy converter is formed ™ ^^ \ d ™ construction and hilliger production