US3609419A - Mechanical resonators for standard frequency oscillators - Google Patents

Mechanical resonators for standard frequency oscillators Download PDF

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Publication number
US3609419A
US3609419A US7008A US3609419DA US3609419A US 3609419 A US3609419 A US 3609419A US 7008 A US7008 A US 7008A US 3609419D A US3609419D A US 3609419DA US 3609419 A US3609419 A US 3609419A
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United States
Prior art keywords
vibrator
primary
bar
vibration
resonator according
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US7008A
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English (en)
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Andre Greuter
Arpad Korom
Peter Donatsch
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GESELLSCHAFT ZURFORDERUNG DER FORSCHUNG AN DER EIDGENOSSISCHEN TECHNISCHEN H OCHSCHULE
ZURFORDERUNG DER FORSCHUNG AN
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ZURFORDERUNG DER FORSCHUNG AN
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    • 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
    • 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
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • 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
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/22—Compensation of mechanisms for stabilising frequency for the effect of variations of temperature
    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C3/00—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means
    • G04C3/08—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means wherein movement is regulated by a mechanical oscillator other than a pendulum or balance, e.g. by a tuning fork, e.g. electrostatically
    • G04C3/10—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means wherein movement is regulated by a mechanical oscillator other than a pendulum or balance, e.g. by a tuning fork, e.g. electrostatically driven by electromagnetic means
    • G04C3/101—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means wherein movement is regulated by a mechanical oscillator other than a pendulum or balance, e.g. by a tuning fork, e.g. electrostatically driven by electromagnetic means constructional details
    • G04C3/102—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means wherein movement is regulated by a mechanical oscillator other than a pendulum or balance, e.g. by a tuning fork, e.g. electrostatically driven by electromagnetic means constructional details of the mechanical oscillator or of the coil

Definitions

  • a mechanical resonator comprising a primary vibrator having a spring member with two axes of symmetry at right angles and two vibration masses coupled to the spring member and arranged to vibrate in mutually opposite senses with the centers of vibration thereof arranged to move on a rectilinear path which coincides with one of said axes.
  • An even number of pairs of secondary vibrators are carried by said primary vibrator with at least one pair of said secondary vibrators associated with each of said vibration masses of the primary vibrator.
  • the centers of vibration of the two secondary vibrators which together form each pair are arranged to move with components of motion parallel to the said axis of symmetry coincident with the path of of the vibration masses of the primary vibration which are in the same sense, and with components of motion at right angles to this axis of symmetry which are mutually opposed.
  • This invention relates to mechanical resonators for standard frequency oscillators, particularly in time-measuring instruments, such a resonator comprising a primary vibrator which includes a spring member with two axes of symmetry at right angles to each other and two vibration masses coupled to the spring member and arranged to vibrate in mutually opposite senses with the centers of vibration thereof arranged to move on a rectilinear path which coincides with one of the axes of symmetry.
  • Vibrators of this kind have been known in various forms for some time and are generally coupled to an electrical oscillator by electromechanical means, so that the vibration frequency of the oscillator conforms to the natural vibration frequency of the mechanical vibrator.
  • Examples of vibrators of this type are to be found in Swiss patent specifications Nos. 406,984 and 414,768 and in US. Pat. No. 1,963,719.
  • the fact that with these known vibrators the centers of vibration of the vibration masses move on a rectilinear path provides the advantage that the natural vibration frequency of the vibrator is unaffected by the influences of the gravitational field and thus does not depend upon the position and orientation of the vibrator in space. This makes this type of vibrator particularly interesting for use in portable instruments, such as wristwatches.
  • the present invention is concerned with the problem of producing a mechanical resonator of the generic type first mentioned above wherein fine tuning is possible without the necessity for adding or removing mass and without changing the spring characteristics of the spring member.
  • a mechanical resonator comprising aprimary vibrator which includes a spring member with two axes of symmetry at right angles to each other and two vibration masses coupled to the spring member and arranged to vibrate in mutually opposite senses with the centers of vibration thereof arranged to move on a rectilinear path which coincides with one of said axes of symmetry, and an even number of pairs of secondary vibrators carried by said primary vibrator with at least one pair of said secondary vibrators associated with each of said vibration masses of the primary vibrator, the centers of vibration of the two secondary vibrators which together form each pair being arranged to move with components of motion parallel to the said axis of symmetry coincident with the path of movement of the vibration masses of the primary vibration which are in the same sense, and with components of motion at right angles to this axis of symmetry which are mutually opposed, and the position of at least one part of each secondary vibrator being adjustable with respect to the primary vibrator to vary the resultant vibration frequency of the resonator.
  • Each secondary vibrator preferably comprises a bar-spring element which is secured at one end to the primary vibrator and at the other end is free.
  • the free end of each bar-spring element may carry one or more terminating masses. Fine tuning of the vibration frequency of the resonator can be effected by moving the terminating masses along the longitudinal axis or axes of the bar-spring elements and/or by pivoting the barspring elements relative to the primary vibrator.
  • one end of the bar-spring element of each secondary vibrator may be secured to a support member which is rotatably connected to the primary vibrator for movement about a pivotal axis perpendicular or parallel to the plane containing the axes of symmetry of the primary vibrator and which remains in any set position.
  • a mass can be pivotably connected to the bar-spring element of each secondary vibrator by means of a pivot pin positioned eccentrically of the center of gravity of the mass so that the mass can be pivoted in relation to the barspring element for fine turning of the vibration frequency of the resonator, and then remains in this set position.
  • FIG. 1 is an axomometric view of a first embodiment of resonator according to the invention
  • FIG. 2 is a plan view of the resonator of FIG. 1;
  • FIG. 3 is a view of the resonator as observed along the line of the axis A and looking towards the resonator;
  • FIG. 3a is a cross-sectional view taken as along the axis A of FIG. 2 but through a slightly modified embodiment of resonator;
  • FIG. 4 is a plan view of a single pair of secondary vibrators of the resonator shown in FIGS. 1 to 3;
  • FIG. 5 is a similar view of a modified form of the pair of secondary vibrators.
  • FIGS. 6 to 11 are plan views each of a modified single pair of secondary vibrators.
  • the mechanical resonator shown in FIGS. 1 to 3 comprises a primary vibrator ll, 12 which consists of a ring-form spring member 11 and two vibration masses 12 secured thereto.
  • the primary vibrator 11, 12 has two axes of symmetry A and B which extend at right angles to each other.
  • a crosspiece 13 extending along the axis of symmetry B serves to secure the spring member 11 to a base (not shown).
  • the two vibration masses 12 are arranged opposite each other so that their centers of gravity lie on the other axis of symmetry A.
  • the masses l2 vibrate to and fro in opposite senses in such manner that their centers of gravity move on a rectilinear path which coincides with the axis of symmetry A.
  • the spring member It thus undergoes flexing oscillations.
  • the spring ring 11 has the shape shown in FIGS. 1 and 2 with alternately concave and convex portions.
  • the ends of the crosspiece 13 are each attached to the center of a convex ring portion, whilst the vibration masses 12 are each rigidly connected to an outwardly projecting tongue 14 at the center of a concave ring portion.
  • This vibrator is known and is described for example in Swiss patent specifications Nos. 414,768 and 450,295.
  • Each projecting tongue 14 of the spring member 11 carries a pin-type support 1, 1' which has a pair of secondary vibrators 2, 3 and 2', 3' respectively mounted thereon.
  • Each vibration mass 12 of the primary vibrator is associated with a pair of these secondary vibrators 2, 3 or 2', 3'.
  • the pin-type supports 1, 1' are each rotatable about an axis c, c which is perpendicular to the plane containing the axes of symmetry A and B, as shown in FIGS. 1 and 3.
  • the secondary vibrators carried by the support 1 each consist of a bar-spring element 2 and a terminating mass 3.
  • the bar-spring element 2 is inserted radially into the support pin 1 so that the longitudinal axis of the bar-spring element 2 extends parallel to the plane containing the axes of symmetry A and B.
  • the mass 3 is carried at the free end of the bar-spring element 2.
  • the two barspring elements 2 which comprise one pair of the secondary vibrators are arranged coaxially and are of the same length. They may be formed from a continuous bar of material which is secured at its center in the support pin 1. Similarly, the two end masses 3 are of the same size and at the same distance away from the axis of rotation c of the support pin.
  • the pair of secondary vibrators carried by the support pin 1' and consisting of the bar-spring element 2 and the end masses 3' is constructed and arranged in a completely symmetrical manner.
  • FIG. 4 shows one pair of secondary vibrators 2, 3 on a larger scale.
  • the support pin 1 has here been rotated about the axis so that the longitudinal axis of the bar-spring elements 2 lies at an angle a to an axis b which extends parallel to the axis of symmetry B and cuts the axis of rotation c.
  • the axis b and its counterpart b on the opposite side of the resonator are both indicated. If the vibration masses 12 of the primary vibrator 11, 12 vibrate in opposite directions, the support pin 1 likewise moves to and fro along the axis A.
  • the secondary vibrators 2, 3 are stimulated to vibrate in a mode which is composed partly of bending vibrations and partly of longitudinal vibrations of the bar-spring elements 2.
  • each end mass 3 can be divided into two components which are respectively parallel to the axes of symmetry A and B.
  • the components of this motion which are parallel to the axis of symmetry A and to the direction of movement of the support pin 1 are directed in the same sense, i.e. are additive, for the two end masses 3 of the particular pair of secondary vibrators, while the components of motion of the same end masses 3 parallel to the axis of symmetry B and to the axis b are opposed to each other.
  • the former components of motion thus have an additive effect on the movement of the adjacent vibration mass 12 of the primary vibrator.
  • the latter components of motion on the other hand cancel each other out in their effect on the primary vibrator.
  • the bar-spring elements 2, for a correctly tuned resonator lie at a considerable angle a to the axis b, so that when finely adjusting the vibration frequency of the resonator, as subsequently becomes necessary, an alteration of the frequency either up and down is possible simply by rotating the pair of secondary vibrators about the axis 0 in one sense or the other.
  • each projecting tongue 14 of the spring member 11 has two pairs of secondary vibrators associated therewith which are located symmetrically on opposite sides of the plane containing the axes of symmetry A and B of the primary vibrator.
  • the support pins 1 and 1' are therefore longer and are mounted so that they project equally from the two sides of the said plane.
  • Each projecting portion of the support pins 1, 1' bears a pair of secondary vibrators of the type described above.
  • two rectilinear bar-spring elements 2 of equal length are clamped coaxially in a common support pin 1.
  • the ends of the bar-spring elements 2 remote from the support pin I carry no terminating masses.
  • the mass of each secondary vibrator thus consists only of the distributed mass of the bar-spring elements 2.
  • all the points of mass of a barspring element 2 can be concentrated into a single point which is referred to as the center of vibration. The same considerations apply to the movement of the center of vibration of the secondary vibrator as were mentioned above with reference to the centers of gravity of the end masses 3.
  • the components of motion parallel to the axis of symmetry A and to the path of motion of the primary vibration masses are directed in the same sense, whilst the components of motion parallel to the other axis of symmetry B and to the axis b are opposed to each other.
  • Tuning of the vibration frequency of the resonator is effected by altering the angle a, i.e. by rotating the support pin 1.
  • each secondary vibrator has its own support pin 1 which if rotatably connected to the spring member of the primary vibrator.
  • the two support pins of the secondary vibrators which together form a pair are arranged at the same distance d along the axis b on respective opposite sides of the axis of symmetry A which coincides with the path of motion of the primary vibration masses.
  • the secondary vibrators each consist of a bar-spring element 2 and a tenninating mass 3, the bar-spring element being radially secured at its one end in the associated support pin 1 and carrying the mass 3 at its other end.
  • the two secondary vibrators which together form a pair are constructed and arranged in mirror image form with respect to the axis of symmetry A, not only with regard to their geometric configuration but also in respect of the spring characteristics and the masses.
  • the two support pins 1 are rotated in opposite senses through approximately the same angle so that the angles a which the barspring elements 2 make with the axis b are altered.
  • the mode of operation of these secondary vibrators is basically the same as described above for the first embodiment.
  • the secondary vibrators again each consist of a bar-spring.element 2 and a mass 3.
  • the two bar-spring elements 2 of the secondary vibrators which together form a pair are arranged coaxially with respect to each other and each have one end mounted in a common support-member 1 which, in contrast to the embodiments described heretofore, is fixedly and not rotatably connected to the spring member of the primary vibrator.
  • the longitudinal axis of the bar-spring elements 2 extends along the axis b at right angles to the axis of symmetry A and to the path of motion of the primary vibration masses.
  • the end masses 3 are displaceable in the longitudinal direction of the bar-spring elements 2.
  • each of the end masses 3 is slidably mounted on its associated bar-spring element and is held in an adjusted position by static friction. If the resonator vibrates, the end masses 3 execute additional vibratory movements on arcuate paths which are centered on the center of the support member 1.
  • the components of movement of the end masses 3 parallel to the axis A are in the same sense and effect the vibration frequency of the resonator, whereas the components of movement parallel to the axis 1: are in opposite senses and have no net effect.
  • the spacings of the two end masses 3 from the support member I are altered at least approximately symmetrically to thereby cause an alteran'on of the natural vibration frequency of the secondary vibrators.
  • FIG. 8 only difiers from the example last described above in that the two bar-spring elements 2 of the secondary vibrators which together form a pair are not mounted coaxially in the support member I but at an angle to each other.
  • the support member 1 is, however, again rigidly connected to the spring member of the primary vibrator.
  • the longitudinal axes of the two bar-spring elements 2 each lie at the same angle a to the axis b. Tuning of the vibration frequency of the resonator is again efiected by moving the masses 3 along the bar-spring elements 2.
  • the masses 3 are fixedly, i.e. nondisplaceably, mounted on the end portions of the bar-spring elements 2 remote from each other, but the adjacent end portions of the bar-spring elements are adjustably held by the support member 1 so that the free length of each bar-spring element can be altered in order to produce the desired tuning of the resonator.
  • the masses 3 can be dispensed with if desired, and, as in the embodiment of FIG. 5, the distributed masses of the bar-spring elements 2 can be used alone.
  • two support members l are arranged at equal distances along the axis b on respective opposite sides of the axis of symmetry A and are rigidly connected to the primary vibrator.
  • a rectilinear barspring elements 2 like a cord is held between the two support members i with the ends of the spring element secured to the support members 1.
  • Two masses 3 are slidably movable on the respective bar-spring elements 2 and will remain in a set position, for example by static friction.
  • a pair of secondary vibrators are used which each consist of a half of the barspring element 2 and one of the masses 3.
  • FIG. 10 illustrates an embodiment wherein the secondary vibrators 2, 3 are both fixedly held by a common support member I which rigidly connected to the primary vibrator.
  • the secondary vibrators comprise coaxially arranged barspring elements 2 which are each secured at their one end in a support member 1.
  • the free end portions of the bar-spring elements 2 each carry a mass 3 which is pivotably connected to the associated spring element by means of a pivot pin 5, positioned eccentrically of the center of gravity of the mass and which is arranged to remain in any adjusted pivoted position.
  • the pivot pins 5 are located at equal distances from the axis of symmetry A on opposite sides thereof.
  • FIG. 11 The embodiment illustrated in FIG. 11 is similar to that shown in FIG. 7, but the end masses 3 are here difierently ar ranged so as to be adjustable on the bar-spring elements 2.
  • the latter each have at their outer end an enlargement 4 provided with an external thread.
  • the end masses 3 are formed as correspondingly threaded nuts which are screwed on to the enlargements 4.
  • Tuning of the vibration frequency of the resonator is effected by rotating the end mass 3 on their enlargements 4 whereby the masses are displaced along the longitudinal axis of the bar-spring elements 2.
  • the secondary vibrators which together form a pair are always arranged so that the oppositely directed components of motion of the center of vibration are parallel to the axis of symmetry B (see FIGS. 1 and 2). From spatial considerations this solution will be the most advantageous in most cases, because then the longitudinal axis or axes of the bar-spring elements 2 extend parallel to the plane which contains the axes of symmetry A and B and in which for the most part the spring member 11 also lies.
  • the arrangement could be so modified that the axes of rotation c, c' of the support pins 1 and 1' coincide respectively with the axes b and b, and the bar-spring elements 2 project on opposite sides of the plane containing the axes of symmetry A and B, e.g. upwards and downwards instead of to the left and right.
  • the bar-spring elements of the secondary vibrators may be advantageous to manufacture from a specially suitable material whose changes in length in response to changes in the ambient temperature cause a change in the natural vibration frequency of the secondary vibrators which counteracts temperature-responsive changes in the natural vibration frequency of the primary vibrator, so that the resultant vibration frequency of the combined resonator is or is at least substantially independent of temperature.
  • the main advantage of the resonator of the present invention is that its vibration frequency can be finely tuned without mass having to be added or removed at any place.
  • This advantage results in economic savings in the production of instruments or devices incorporating the resonator since tuning can be carried out more quickly and by less skilled personnel. Furthermore, there is practically no waste from inappropriate filing away of material. Since tuning can be repeated as often as desired, an important advantage of the resonator lies in the possibility of easy retuning if displace ment of the vibration frequency of the resonator arises, e.g. through wear or other factors. The tuning and retuning can also be carried out by relatively unskilled persons.
  • each secondary vibrator comprises a bar-spring element which is secured at its end to the primary vibrator and is free at its other end.
  • each bar-spring element carries at least one mass.
  • a resonator according to claim 3 wherein said mass is displaceable along the longitudinal axis of the bar-spring element.
  • a resonator according to claim 3 wherein said mass and a part of the bar-spring element have engaging threads.
  • a resonator according to claim 3 wherein said mass is slidable on the bar-spring element and is held in position by static friction.
  • each bar-spring element is secured to a support member secured to the primary vibrator and is arranged to be displaceable along its longitudinal axis.
  • each two secondary vibrators which together form a pair comprise two coaxially arranged bar-spring elements having their adjoining ends connected to a common support member secured to the primary vibrator.
  • each two ,8 secondary vibrators which together form a pair comprise two bar-spring elements respectively located on opposite sides of the path of movement of the primary vibration masses and symmetrically disposed with respect to said path.
  • each secondary vibrator is rotatable relative to the primary vibrator about an axis perpendicular to the path of movement of the vibration masses of the primary vibrator and is adapted to remain in any set position.
  • a resonator according to claim 2 wherein one end of the bar-spring element of each secondary vibrator is secured in a support member which is rotatably connected to the primary vibrator for rotation about an axis perpendicular to the path of movement of the primary vibration masses and adapted to remain in any set position.
  • each of the symmetrically disposed bar-spring elements of the secondary vibrators which together form a pair is mounted on its own support member which is rotatably connected to the primary vibrator for rotation about an axis perpendicular to the path of movement of the primary vibration masses and is adapted to remain in any set position, and said support members being rotatable about respective separate axes which are at equal distances from the path of motion of the primary vibration masses.
  • a resonator according to claim 1 wherein the secondary vibrators each have at least one portion whose dimension alter in dependence on the ambient temperature to thereby create changes in the natural frequency of the secondary vibrator which counteract temperature responsive changes in the natural vibration frequency of the primary vibrator.
  • each secondary vibrator comprises a bar-spring element which is secured at its one end to the primary vibrator and is free at its other end, and wherein the bar-spring element of each secondary vibrator is the portion thereof which alters with changes in temperature.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Metallurgy (AREA)
  • Electromagnetism (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Electric Clocks (AREA)
US7008A 1969-02-05 1970-01-30 Mechanical resonators for standard frequency oscillators Expired - Lifetime US3609419A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH172869A CH486164A (de) 1969-02-05 1969-02-05 Mechanischer Resonator für Normalfrequenzoszillatoren

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US3609419A true US3609419A (en) 1971-09-28

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US7008A Expired - Lifetime US3609419A (en) 1969-02-05 1970-01-30 Mechanical resonators for standard frequency oscillators

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US (1) US3609419A (de)
AT (1) AT290404B (de)
CH (2) CH486164A (de)
DE (1) DE2005306B2 (de)
FR (1) FR2030312B1 (de)
GB (1) GB1288863A (de)
NL (1) NL7001683A (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130221767A1 (en) * 2012-02-23 2013-08-29 Nidec Seimitsu Corporation Vibration generator
CN108375891A (zh) * 2017-01-31 2018-08-07 精工电子有限公司 温度补偿型游丝摆轮、机芯以及钟表
US20200295647A1 (en) * 2018-10-24 2020-09-17 Mplus Co., Ltd. Sound vibration actuator
US20210399617A1 (en) * 2019-03-12 2021-12-23 Alps Alpine Co., Ltd. Electromagnetic drive device and operation device
US20220360156A1 (en) * 2021-05-06 2022-11-10 Aac Microtech (Changzhou) Co., Ltd. Linear vibration motor
US11784548B2 (en) * 2019-12-11 2023-10-10 Meta Platforms, Inc. Vibrating actuator with two resonant frequencies and two moving parts

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2020384B1 (en) * 2018-02-06 2019-08-14 Flexous Mech Ip B V Mechanical watch oscillator

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130221767A1 (en) * 2012-02-23 2013-08-29 Nidec Seimitsu Corporation Vibration generator
US9024489B2 (en) * 2012-02-23 2015-05-05 Nidec Seimitsu Corporation Vibration generator
CN108375891A (zh) * 2017-01-31 2018-08-07 精工电子有限公司 温度补偿型游丝摆轮、机芯以及钟表
CN108375891B (zh) * 2017-01-31 2021-06-15 精工电子有限公司 温度补偿型游丝摆轮、机芯以及钟表
US20200295647A1 (en) * 2018-10-24 2020-09-17 Mplus Co., Ltd. Sound vibration actuator
US11489427B2 (en) * 2018-10-24 2022-11-01 Mplus Co., Ltd. Sound vibration actuator with three vibration assemblies and different frequencies
US20210399617A1 (en) * 2019-03-12 2021-12-23 Alps Alpine Co., Ltd. Electromagnetic drive device and operation device
US11909290B2 (en) * 2019-03-12 2024-02-20 Alps Alpine Co., Ltd. Electromagnetic drive device and operation device
US11784548B2 (en) * 2019-12-11 2023-10-10 Meta Platforms, Inc. Vibrating actuator with two resonant frequencies and two moving parts
US20220360156A1 (en) * 2021-05-06 2022-11-10 Aac Microtech (Changzhou) Co., Ltd. Linear vibration motor
US11831215B2 (en) * 2021-05-06 2023-11-28 Aac Microtech (Changzhou) Co., Ltd. Linear vibration motor

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Publication number Publication date
DE2005306B2 (de) 1971-07-22
GB1288863A (de) 1972-09-13
FR2030312B1 (de) 1973-07-13
CH511469A (de) 1971-02-26
DE2005306A1 (de) 1970-09-24
NL7001683A (de) 1970-08-07
FR2030312A1 (de) 1970-11-13
CH486164A (de) 1970-02-15
AT290404B (de) 1971-06-11

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