WO2009104475A1 - Vibration generator - Google Patents

Vibration generator Download PDF

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Publication number
WO2009104475A1
WO2009104475A1 PCT/JP2009/051893 JP2009051893W WO2009104475A1 WO 2009104475 A1 WO2009104475 A1 WO 2009104475A1 JP 2009051893 W JP2009051893 W JP 2009051893W WO 2009104475 A1 WO2009104475 A1 WO 2009104475A1
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WO
WIPO (PCT)
Prior art keywords
spring
end side
fixed
main spring
ring portion
Prior art date
Application number
PCT/JP2009/051893
Other languages
French (fr)
Japanese (ja)
Inventor
雅春 加賀美
和隆 坂口
勇樹 高橋
繁典 稲本
Original Assignee
ミツミ電機株式会社
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Application filed by ミツミ電機株式会社 filed Critical ミツミ電機株式会社
Publication of WO2009104475A1 publication Critical patent/WO2009104475A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/02—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy
    • B06B1/04—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with electromagnetism
    • B06B1/045—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with electromagnetism using vibrating magnet, armature or coil system
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K33/00—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system
    • H02K33/02—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system with armatures moved one way by energisation of a single coil system and returned by mechanical force, e.g. by springs
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa

Definitions

  • the present invention relates to a vibration generator.
  • vibration generators are used in operation devices such as mobile terminals such as mobile phones and PDAs, and game controllers.
  • a vibration generator for such use as described in Patent Documents 1 and 2, those having the following configurations and functions are used. That is, a first movable element constituted by a magnet and a yoke supported by a leaf spring and a stator constituted by a coil fixed to the casing, or a coil fixed to the diaphragm instead of this stator. And a second movable element.
  • the first mover generates vibration and the second mover generates sound by the action of the magnetic force generated by the magnet and the electromagnetic force generated by the current flowing in the coil.
  • this type of vibration generator employs a system in which a coil is energized with a frequency substantially the same as the resonance frequency of a vibration system composed of a leaf spring and a mover to resonate the vibration system ( Patent Document 3).
  • FIG. 16 shows a frequency characteristic diagram of the vibration force [N] obtained by a conventional vibration generator using a steel plate spring.
  • the frequency characteristic of the vibration generator is shown by a sharp curve with the resonance frequency as the peak, and a large vibration force can be obtained at the resonance frequency, but the input frequency is resonant. As the frequency deviates, the vibration force obtained becomes weaker. Therefore, the practicality in the high band and the low band is not high than the resonance frequency, and the use is limited to the vicinity of the resonance frequency. Since the human sense of vibration depends on the frequency, the optimal vibration frequency differs depending on the application, and there is a problem that the vibration of a single frequency lacks expressive power. Therefore, there is a problem of improvement to frequency characteristics (flattening of frequency characteristic curves) with little change depending on frequency over a wide band. Such improvement can improve the practical use in a wide band.
  • Patent Document 4 describes various resin materials as a material for the spring that supports the mover, and also adopts a layer structure of different materials.
  • Patent Document 5 describes a spring in which a first spring and a second spring are connected in series. As materials for the first spring and the second spring, an elastic body such as a metal thin plate, rubber, or resin is cited. Yes.
  • Patent Document 6 describes that an arm part is connected to an inner peripheral part and an outer peripheral part via an elastic joint part, and the elastic joint part and the arm part are made of an elastomer material having different hardness.
  • Japanese Patent No. 3375233 JP 2003-9495 A Japanese Patent Laid-Open No. 9-205763 JP 2005-303895 A Japanese Patent Laid-Open No. 10-14195 JP 2004-229173 A
  • the frequency characteristics of the vibration system can be selected by selecting and combining the materials.
  • the series connection structure and layer structure it is small and thin.
  • it is not suitable for easy production, and it is desired to improve the frequency characteristics while considering the reduction in size and thickness and ease of production.
  • the present invention has been made in view of the above problems in the prior art, and is a combination spring that can be easily reduced in size and thickness, can be easily manufactured, and can easily change the frequency characteristics of a vibration system including a spring and a mover. It is an object of the present invention to provide a vibration generator having
  • the invention according to claim 1 for solving the above-mentioned problems is a coil fixed to a diaphragm or other member at one end in the central axis direction, and vibrates in the central axis direction facing the coil from the other end side.
  • a mover composed of a magnet and a yoke, a combination spring that elastically supports the mover so as to vibrate in the central axis direction, and a housing that houses the coil, the mover, and the combination spring.
  • a part of the yoke constitutes a yoke outer peripheral portion disposed on the outer side in the radial direction of the coil
  • the combination spring has a main spring and an auxiliary spring
  • the main spring includes an outer peripheral ring portion fixed to the casing, and an inner peripheral ring portion disposed on the radially outer side with respect to the outer peripheral ring portion and fixed to the outer peripheral portion of the yoke.
  • the main spring is composed of one fixed end side end, one arm part continuous with the fixed end side, and one movable end side end continuous with the arm part.
  • the auxiliary spring is made of a material different from the main spring, The auxiliary spring is between the fixed end side end and the fixed end side end and another set of the movable end side end adjacent to the circumferential direction opposite to the constant circumferential direction, or the inner
  • the vibration generating device is provided between the peripheral ring portion and the arm portion and attached to the main spring.
  • the invention according to claim 2 is the vibration generator according to claim 1, wherein the loss coefficient of the combination spring is larger than the loss coefficient of the main spring.
  • the invention according to claim 3 is the vibration generating device according to claim 1 or 2, wherein a spring constant of the combination spring is made larger than a spring constant of the main spring.
  • the invention according to claim 4 is the vibration generator according to any one of claims 1 to 3, wherein the main spring is made of a metal plate and the auxiliary spring is made of a polymer material. .
  • the fixed part of the main spring is constituted by the outer ring part and the inner ring part
  • the elastic deformation part of the main spring is constituted by the fixed end side end part, the arm part and the movable end side end part. Since the auxiliary spring is hung between the fixed end side end portion and the movable end side end portion adjacent thereto, the auxiliary spring can be configured simply with a relatively small piece of auxiliary spring. Further, with such a relatively small piece of material, an auxiliary spring can be provided in parallel with the arm portion between the fixed end side end portion and the movable end side end portion having a large displacement.
  • auxiliary spring can be attached in parallel with the arm part between the fixed end side end part and the movable end side end part with large displacement, the loss coefficient (and hence the damping factor) of the entire combined spring is effectively increased. Or the spring constant of the entire combination spring can be effectively increased.
  • a relatively small piece of auxiliary spring is attached in parallel to the main spring within the interval between the outer ring part and the inner ring part, thereby fixing the outer ring part and the housing and the inner ring part and the outer circumference of the yoke.
  • a combination spring having favorable characteristics without interfering with the fixing with the portion and without increasing the size due to an increase in the space required in the radial direction.
  • it can be manufactured by attaching an auxiliary spring to the main spring and further selecting the material of the auxiliary spring without breaking the situation where a vibration generator using only the main spring can be obtained without using the auxiliary spring. It is possible to obtain a vibration generator having a combination spring with various characteristics with good characteristics.
  • the frequency characteristics of the vibration system composed of the spring and the mover can be easily changed according to the present invention. There is an effect that a vibration generating device having a combination spring capable of selecting the characteristics can be obtained.
  • FIG. 1 is a perspective view of a vibration generator according to an embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the vibration generator according to the embodiment of the present invention.
  • 3 and 4 are plan views of the main spring used in the vibration generator according to the embodiment of the present invention.
  • FIG. 5 is a vertical cross-sectional view of a vibration generating apparatus according to an embodiment of the present invention.
  • the vibration generator 1 according to the present embodiment includes a base housing 2, a coil 3, a center yoke 4, a magnet 5, a main spring 6, an outer yoke 7, and an upper portion.
  • An outer peripheral housing 8a, a lower outer peripheral housing 8b, and an auxiliary spring 9 are provided.
  • the center yoke 4, the magnet 5, and the outer yoke 7 constitute a mover.
  • the main spring 6 and the auxiliary spring 9 constitute a combination spring.
  • the main spring 6 is made of a metal plate, and the auxiliary spring 9 is made of a polymer material.
  • the coil 3 is configured as a stator.
  • the coil 3 is fixed to the center of the circular plate member 2 a of the base housing 2.
  • the circular plate member 2a may be movably supported with respect to the casing body so that the circular plate member 2a becomes a diaphragm. In this case, the coil 3 serves as the second movable element described above.
  • each part is formed in a circular shape and is arranged concentrically around the central axis C of the coil 3.
  • One end side where the coil 3 is fixed along the central axis C is indicated by an arrow A, and the other end side is indicated by an arrow B.
  • the mover composed of the center yoke 4, the magnet 5, and the outer yoke 7 is disposed so as to face the coil 3 from the other end side (B side).
  • the main spring 6 elastically supports the movable element so as to vibrate in the direction of the central axis C.
  • the center yoke 4 and the magnet 5 are smaller than the inner diameter of the coil 3 and are formed in a disk or a column shape having substantially the same diameter.
  • the central portion 7 a of the outer yoke 7 is formed in a disk shape larger than the outer diameter of the coil 3.
  • One end side and the other end side of the magnet 5 constitute opposite magnetic poles.
  • the center yoke 4 is joined to one end side (A side) of the magnet 5.
  • the central portion 7 a of the outer yoke 7 is joined to the other end side (B side) of the magnet 5.
  • the outer yoke 7 constitutes a yoke outer peripheral portion 7b continuous with the central portion 7a.
  • the yoke outer peripheral portion 7b protrudes from the central portion 7a at one end side (A side) and is formed on the same surface as the central portion 7a at the other end side (B side).
  • the dimension in the central axis direction is larger than that of the portion 7a.
  • the center yoke 4 is disposed inside the coil 3 in the radial direction.
  • the yoke outer peripheral portion 7 b is disposed outside the coil 3 in the radial direction.
  • the main spring 6 is disposed outside the coil 3 in the radial direction, and extends in the radial direction.
  • the upper outer casing 8a and the lower outer casing 8b are connected to each other in a cylindrical shape having the same diameter, and are fixed to the casing with an outer peripheral ring portion 6a of the main spring 6 interposed therebetween.
  • On the end face on one end side (A side) of the yoke outer peripheral portion 7b a step is formed by cutting out the outer peripheral side, and the inner peripheral ring portion 6b of the main spring 6 is disposed so as to fill the step, and the inner peripheral ring portion 6b is fixed to the yoke outer peripheral portion 7b.
  • the main spring 6 is a ring-shaped leaf spring in which an outer peripheral ring portion 6a and an inner peripheral ring portion 6b are each formed in a ring shape and are arranged at intervals in the radial direction. That is, when the inner diameter of the outer ring part 6a is made larger than the outer diameter of the inner ring part 6b, the two are spaced apart in the radial direction.
  • An elastic deformation portion constituted by the fixed end side end portion 6d, the arm portion 6c and the movable end side end portion 6e is disposed at the interval, and the outer peripheral ring portion 6a and the inner peripheral ring portion 6b are connected.
  • the fixed end 6d is formed so as to protrude radially inward from the inner periphery of the outer ring portion 6a.
  • the movable end side end portion 6e is formed to protrude radially outward from the outer periphery of the inner peripheral ring portion 6b.
  • the arm portion 6c extends from the fixed end side end portion 6d in a constant circumferential direction around the central axis C (counterclockwise direction in FIGS. 3 and 4) and is connected to the movable end side end portion 6e.
  • the protruding width 6f of the fixed end 6d is larger than the width 6g of the arm 6c.
  • the protrusion width 6h of the movable end side end portion 6e is larger than the width 6g of the arm portion 6c and smaller than the protrusion width 6f of the fixed end side end portion 6d.
  • the spiral groove 6k has a uniform and narrow groove width.
  • the spiral groove 6k includes an outer peripheral groove 6k-1 and an inner peripheral groove 6k-2 that extend in the circumferential direction at different radial positions, and a radial groove 6k-3 that connects these ends and extends in the radial direction. Is done.
  • An outer peripheral groove 6k-1 extends in the circumferential direction continuously to the outer end of the radial groove 6k-3.
  • An inner circumferential groove 6k-2 extends in the circumferential direction continuously to the inner end of the radial groove 6k-3.
  • a compact ring-shaped leaf spring in which the distance between the outer ring portion 6a and the inner ring portion 6b is short can be configured.
  • the main spring 6 is formed by dividing a set of one fixed end side end portion 6d, one arm portion 6c continuous therewith and one movable end side end portion 6e continuous thereto into three portions.
  • the inner ring portion 6b is supported by the three arms by arranging one set in the angular region by 120 degrees which can be different. It is good also as 4 arms or more instead of 3 arms. The reason for using three or more arms is to stably support the vibration axis of the mover so that it does not shake.
  • each of the three auxiliary springs 9, 9, 9 has a fixed end side end portion 6d and a circumferential direction opposite to the fixed end side end portion 6d (see FIGS. 3 and 5). 4 is attached to the main spring 6 between the other end 6e of the movable end side adjacent in the clockwise direction (4). Both ends of the auxiliary spring 9 are affixed and fixed to the fixed end side end 6d and the movable end side end 6e.
  • FIG. 5 shows a cross section of the combined spring composed of the main spring 6 and the auxiliary spring 9 cut along the line DD shown in FIG.
  • the vibration generator 1 has the above-described configuration, and when driving power is input to the coil 3, the mover including the center yoke 4, the magnet 5, and the outer yoke 7 vibrates in the direction of the central axis C.
  • the frequency characteristics of the vibration system composed of the spring and the mover can be easily changed, and thus the characteristics can be easily changed.
  • a vibration generating apparatus having a combination spring that can be improved or selected according to application can be obtained.
  • the damping rate and spring constant of the combined spring are increased, and the frequency characteristics with little frequency variation over a wide band are improved (frequency characteristic curve is flattened). The practicality in a wide band can be improved. Examples 1 and 2 and examples of use are shown below.
  • FIG. 6 is a table in which the spring constants of the main spring, the auxiliary spring, and the combination spring according to Examples 1 and 2 and the loss coefficients of the main spring and the combination spring are described.
  • Example 1 has an outer diameter of ⁇ 60 [mm] and a resonance frequency of 37.2 [Hz]
  • Example 2 has an outer diameter of ⁇ 24 [mm] and a resonance frequency of 52 [Hz]. Both 1 and 2 follow the above embodiment.
  • the auxiliary spring used the tape created by apply
  • FIG. 7A shows the definition of the Q value.
  • the Q value is a value representing the sharpness of resonance and is also called sharpness.
  • the increase in the loss factor ⁇ in both Examples 1 and 2 can reduce the Q value, that is, suppress the resonance peak.
  • FIG. 8 is a frequency characteristic diagram of the displacement gain [mm / V] of the mover according to the first embodiment
  • FIG. 9 is a frequency characteristic diagram of the vibration force [N] of the mover according to the first embodiment
  • FIG. It is a frequency characteristic figure of displacement [mm] of a needle concerning concerning.
  • 11 is a frequency characteristic diagram of the displacement gain [mm / V] of the mover according to the second embodiment
  • FIG. 12 is a frequency characteristic diagram of the vibration force [N] of the mover according to the second embodiment
  • FIG. It is a frequency characteristic figure of displacement [mm] of a needle concerning concerning. 8 to 13, the broken line curve is a conventional example for comparison.
  • the whole spring applied to each conventional example has the characteristics of the main spring shown in the table of FIG. Since the first and second embodiments of the present invention have a larger spring constant, as shown in FIGS. 10 and 13, the first and second embodiments of the present invention have the same maximum amplitude as the conventional example.
  • the driving power input to the coil is made larger than that of the conventional example.
  • the maximum gain Gmax is about 2.3 times the DC gain G1, which is greatly suppressed as compared with the conventional example.
  • the base of the characteristic curve is broader (that is, the inclined line from the peak becomes gentler) than in the conventional example, and both the high band and the low band with respect to the resonance frequency.
  • the vibration force is improved.
  • the amplitude displacement is improved particularly in the low band with respect to the resonance frequency as compared with the conventional example.
  • the maximum gain Gmax is about 1.4 times the DC gain G1, which is much smaller than the conventional example.
  • the base of the characteristic curve is broadened (that is, the inclined line from the peak becomes gentle), both in the high band and the low band with respect to the resonance frequency.
  • the vibration force is improved.
  • the amplitude displacement is improved particularly in the low band with respect to the resonance frequency as compared with the conventional example.
  • the Q values of the three frequency characteristics are small in both the first and second embodiments, and the frequency characteristic curve is flattened.
  • the frequency characteristic curve is flattened, that is, the frequency characteristic with little change depending on the frequency over a wide band is improved, so that the practicality of the vibration generator in the wide band is widened.
  • the maximum amplitude can be suppressed in the present invention, so that the input voltage can be increased to such an extent that interference between components does not occur.
  • the present invention even if the allowable movable range of the mover is the same, according to the present invention, it is possible to increase the input voltage as compared with the conventional case, and as a result, it is possible to obtain a large vibration force in a wider band than the conventional case. Therefore, it is possible to use the conventional vibration generator limited to use in the vicinity of the resonance frequency in a wide band.
  • the output drop in the high band and the low band with respect to the resonance frequency is improved. Since it can be used in a wide band, the expressive power by vibration including voice output is improved.
  • the bottom of the base housing 2 described above is attached to a board or panel (including the housing of the parent device on which the vibration generating device is mounted) to generate the vibration generated by the vibration generating device.
  • a board or panel including the housing of the parent device on which the vibration generating device is mounted
  • an audio output device using the board or panel as a diaphragm can be configured. Compared to the prior art, it is possible to obtain a large sound output in both the high and low sound ranges, and the utility expands from the low sound output to the high sound output.
  • FIG. 14 is a frequency characteristic diagram of the sound pressure level (SPL) [dbSPL] of the mover according to the first embodiment.
  • SPL sound pressure level
  • the resonance frequency represented by [1 / (2 * ⁇ )] * ⁇ (K / m) is set to about 40 [Hz]. It has become possible to output audio in a wide band from lower to over 10,000 [Hz].
  • the vibration generator that uses the lowest frequency in the desired frequency band or a frequency lower than the lowest value as the resonance frequency, it is possible to output sound in the desired frequency band.
  • FIG. 15A is a perspective view of an example mobile communication device 11 equipped with the vibration generator 1 of the present embodiment.
  • the bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing of the mobile communication device 11.
  • this vibration generator 1 since it is driven in a wide band and can output a wide-band vibration, the vibration expressing power is improved, and for example, it is possible to select a ringing vibration in a band that is most easily felt by each user. For example, it is possible to generate a ringing vibration in a band according to the user's preference.
  • FIG. 15B is a perspective view of an example amusement device 12 equipped with the vibration generator 1 of the present embodiment.
  • the bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing by a grip portion of the amusement device 12.
  • this vibration generator 1 since it is driven in a wide band and can output a wide-band vibration, the vibration expressive power is improved. For example, a difference between a feeling of shooting with a large gun and a feeling of shooting with a small gun in a shooting game Can be expressed by changing the vibration frequency, so that the user can have a more realistic game experience. *
  • FIG. 15C is a perspective view of an example touch panel type information input device 13 equipped with the vibration generator 1 of the present embodiment.
  • the bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing on the back of the operation unit of the touch panel type information input device 13.
  • the vibration generating device 1 since it is driven in a wide band and can output a wide-band vibration, the vibration expressing power is improved. For example, when an operation button image is pressed, an operation like a mechanical operation button is performed.
  • Various feelings can be expressed more realistically, such as being able to express a feeling.
  • FIG. 15D is a perspective view of an example audio output device 14 equipped with the vibration generator 1 of the present embodiment.
  • the bottom surface of the base housing 2 of the vibration generator 1 is fixed to the panel back surface of the audio output device 14.
  • this vibration generator 1 since it can be driven in a wide band and can output a wide band vibration, it is possible to generate a frequency vibration of the input audio signal by inputting the audio signal. Therefore, by attaching the vibration generating device 1 to a panel or casing of any device, the sound generating device 1 is used as a sound source, and the sound output device (sound (Equipment with output function) can be configured.
  • auxiliary spring may be installed between the inner ring portion 6b and the arm portion 6c instead of the installation position of the above embodiment. In this case, by moving the construction position of the auxiliary spring along the circumferential direction, the effectiveness of the same auxiliary spring can be freely selected.
  • It can be used as a vibration or sound generator.
  • it can be used as a sound generation source of a vibration generator mounted on a mobile communication device such as a mobile phone, an amusement device such as a game controller, a touch panel type information input device, or a sound output device.

Abstract

Provided is a vibration generator suitable for compaction and thinning, and for facilitation of manufacture and having a combination spring which can alter the frequency characteristics of a vibration system consisting of a spring and a moving element easily. A combination spring in a vibration generator (1) has a main spring (6), and an auxiliary spring (9) made of a material different from that of the main spring (6). The main spring has an outer circumferential ring portion (6a) fixed for a housing (8a, 8b), an inner circumferential ring portion (6b) spaced apart radially inward from the outer circumferential ring portion and fixed to the outer circumferential portion (7b) of a yoke, an end portion (6d) on the fixed end side formed to project radially inward from the inner circumference of the outer circumferential ring portion, an end portion (6e) on the movable end side formed to project radially outward from the outer circumference of the inner circumferential ring portion, and an arm portion extending in a predetermined circumferential direction around the central axis (C) from the end portion on the fixed end side and leading to the end portion on the movable end side. The auxiliary spring is stretched between the end portion on the fixed end side and the end portion on the movable end side contiguous to the end portion on the fixed end side in the circumferential direction reverse to the predetermined circumferential direction, or between the inner circumferential ring portion and the arm portion.

Description

振動発生装置Vibration generator
　本発明は、振動発生装置に関する。 The present invention relates to a vibration generator.
　近時、携帯電話やＰＤＡなどの携帯端末、ゲーム用コントローラなど操作機器に振動発生装置が用いられている。
　かかる用途の振動発生装置としては、特許文献１、２にも記載されるように、次のような構成、作用を有するものが利用されている。
　すなわち、板バネにより支持されたマグネット及びヨークにより構成される第１可動子と、筐体に固定されたコイルにより構成される固定子、又はこの固定子に代え振動板に固定されたコイルにより構成される第２可動子とを備えて構成される。
　そして、マグネットにより発生する磁力とコイルに流れる電流により発生する電磁力との作用により、第１可動子が振動を発生し、第２可動子が音響を発生する。 Recently, vibration generators are used in operation devices such as mobile terminals such as mobile phones and PDAs, and game controllers.
As a vibration generator for such use, as described in Patent Documents 1 and 2, those having the following configurations and functions are used.
That is, a first movable element constituted by a magnet and a yoke supported by a leaf spring and a stator constituted by a coil fixed to the casing, or a coil fixed to the diaphragm instead of this stator. And a second movable element.
The first mover generates vibration and the second mover generates sound by the action of the magnetic force generated by the magnet and the electromagnetic force generated by the current flowing in the coil.
　従来、この種の振動発生装置は、板バネと可動子とで構成される振動系の共振周波数とほぼ同一の周波数をコイルに通電して、前記振動系を共振させる方式が採用されている（特許文献３）。 Conventionally, this type of vibration generator employs a system in which a coil is energized with a frequency substantially the same as the resonance frequency of a vibration system composed of a leaf spring and a mover to resonate the vibration system ( Patent Document 3).
　図１６に、鋼製板バネを使用した従来の振動発生装置により得られる振動力〔Ｎ〕の周波数特性図を示した。
　図１６に示されるように、振動発生装置の周波数特性は、共振周波数をピークとした尖鋭な曲線により示されており、共振周波数では大きな振動力を得ることが可能であるが、入力周波数が共振周波数から外れるにつれて得られる振動力は弱くなってしまう。したがって、共振周波数より高帯域及び低帯域での実用度は高くなく、もっぱら共振周波数付近での使用に限定される。
　振動に対する人体の感覚は周波数に依存することから、使用用途により最適な振動周波数は異なり、また、単一振動数の振動では表現力に欠けるという問題がある。
　したがって、広帯域に亘って周波数に依る変化の少ない周波数特性への改善（周波数特性曲線の平坦化）が課題となる。かかる改善により広帯域での実用度を向上することができる。 FIG. 16 shows a frequency characteristic diagram of the vibration force [N] obtained by a conventional vibration generator using a steel plate spring.
As shown in FIG. 16, the frequency characteristic of the vibration generator is shown by a sharp curve with the resonance frequency as the peak, and a large vibration force can be obtained at the resonance frequency, but the input frequency is resonant. As the frequency deviates, the vibration force obtained becomes weaker. Therefore, the practicality in the high band and the low band is not high than the resonance frequency, and the use is limited to the vicinity of the resonance frequency.
Since the human sense of vibration depends on the frequency, the optimal vibration frequency differs depending on the application, and there is a problem that the vibration of a single frequency lacks expressive power.
Therefore, there is a problem of improvement to frequency characteristics (flattening of frequency characteristic curves) with little change depending on frequency over a wide band. Such improvement can improve the practical use in a wide band.
　板バネと可動子とで構成される振動系の周波数特性は、可動部重量・バネ定数・振動系の減衰特性に依存する。可動部重量は製品の大きさにより限界が決まり、設計自由度が低い。したがって、上記課題を解決するため、板バネの材料の選択、組合せを試みることが得策である。
　特許文献４には、可動子を支持するバネの材料として、種々の樹脂材料を挙げるとともに、異なる素材の層構造を採用することも記載されている。
　特許文献５には、第１バネと第２バネとを直列に繋げて組み合わせたバネが記載され、第１バネ及び第２バネの材料として、金属薄板、ゴム、樹脂等の弾性体を挙げている。
　特許文献６には、弾性接合部を介してアーム部を内周部及び外周部に連結し、弾性接合部とアーム部とを硬度のことなるエラストマー材で構成することが記載されている。
特許第３３７５２３３号公報 特開２００３－９４９５号公報 特開平９－２０５７６３号公報 特開２００５－３０３８９５号公報 特開平１０－１４１９５号公報 特開２００４－２２９１７３号公報 The frequency characteristic of the vibration system composed of the leaf spring and the mover depends on the weight of the movable part, the spring constant, and the damping characteristic of the vibration system. The moving part weight is limited by the size of the product, and the degree of freedom in design is low. Therefore, in order to solve the above problems, it is advantageous to try selection and combination of the material of the leaf spring.
Patent Document 4 describes various resin materials as a material for the spring that supports the mover, and also adopts a layer structure of different materials.
Patent Document 5 describes a spring in which a first spring and a second spring are connected in series. As materials for the first spring and the second spring, an elastic body such as a metal thin plate, rubber, or resin is cited. Yes.
Patent Document 6 describes that an arm part is connected to an inner peripheral part and an outer peripheral part via an elastic joint part, and the elastic joint part and the arm part are made of an elastomer material having different hardness.
Japanese Patent No. 3375233 JP 2003-9495 A Japanese Patent Laid-Open No. 9-205763 JP 2005-303895 A Japanese Patent Laid-Open No. 10-14195 JP 2004-229173 A
　上掲した特許文献４～６に記載の組合せバネにあっては、材料の選択、組合せにより振動系の周波数特性を選択することができるが、直列の連結構造や層構造によるため、小型薄型化もしくは製作の容易に適しておらず、小型薄型化、製作の容易に配慮しつつ上記周波数特性の改善を図ることが望まれる。 In the combination springs described in Patent Documents 4 to 6, the frequency characteristics of the vibration system can be selected by selecting and combining the materials. However, because of the series connection structure and layer structure, it is small and thin. Alternatively, it is not suitable for easy production, and it is desired to improve the frequency characteristics while considering the reduction in size and thickness and ease of production.
　本発明は以上の従来技術における問題に鑑みてなされたものであって、小型薄型化、製作の容易に適し、バネと可動子とで構成される振動系の周波数特性を容易に変更できる組合せバネを有した振動発生装置を提供することを課題とする。 The present invention has been made in view of the above problems in the prior art, and is a combination spring that can be easily reduced in size and thickness, can be easily manufactured, and can easily change the frequency characteristics of a vibration system including a spring and a mover. It is an object of the present invention to provide a vibration generator having
　以上の課題を解決するための請求項１記載の発明は、中心軸方向の一端において振動板その他の部材に固定されたコイルと、前記コイルに対してその他端側から臨み前記中心軸方向に振動するマグネット及びヨークにより構成される可動子と、前記可動子を前記中心軸方向に振動可能に弾性支持する組合せバネと、前記コイル、前記可動子及び前記組合せバネを収める筐体とを備え、
前記ヨークの一部は前記コイルの径方向の外側に配置されるヨーク外周部を構成し、
前記組合せバネは、主バネと、補助バネとを有し、
前記主バネは、前記筐体に対して固定された外周リング部と、前記外周リング部に対して前記径方向内側に間隔を隔てて配置され前記ヨーク外周部に固定された内周リング部と、前記外周リング部の内周から前記径方向内側に突出形成された固定端側端部と、前記内周リング部の外周から前記径方向外側に突出形成された可動端側端部と、前記固定端側端部から前記中心軸周りの一定の周方向に延出し前記可動端側端部に繋がるアーム部とを有し、
前記主バネは、１つの前記固定端側端部、これに連続する１つの前記アーム部及びこれに連続する１つの前記可動端側端部とからなる組を、一周を３以上に分割してできる異なる角度領域に１組ずつ配して前記内周リング部を３アーム以上で支持し、
前記補助バネは、前記主バネと異なる材料により構成され、
前記補助バネが、前記固定端側端部と、当該固定端側端部と前記一定の周方向と逆の周方向に隣接する他の組の前記可動端側端部との間、又は前記内周リング部と前記アーム部との間に架けられ前記主バネに付設されてなる振動発生装置である。 The invention according to claim 1 for solving the above-mentioned problems is a coil fixed to a diaphragm or other member at one end in the central axis direction, and vibrates in the central axis direction facing the coil from the other end side. A mover composed of a magnet and a yoke, a combination spring that elastically supports the mover so as to vibrate in the central axis direction, and a housing that houses the coil, the mover, and the combination spring.
A part of the yoke constitutes a yoke outer peripheral portion disposed on the outer side in the radial direction of the coil,
The combination spring has a main spring and an auxiliary spring,
The main spring includes an outer peripheral ring portion fixed to the casing, and an inner peripheral ring portion disposed on the radially outer side with respect to the outer peripheral ring portion and fixed to the outer peripheral portion of the yoke. A fixed end side end projecting from the inner periphery of the outer ring portion to the radially inner side, a movable end side end projecting from the outer periphery of the inner ring portion to the radially outer side, An arm portion extending from a fixed end side end portion in a certain circumferential direction around the central axis and connected to the movable end side end portion;
The main spring is composed of one fixed end side end, one arm part continuous with the fixed end side, and one movable end side end continuous with the arm part. One set is arranged in different angular areas that can be supported and the inner ring part is supported by three or more arms,
The auxiliary spring is made of a material different from the main spring,
The auxiliary spring is between the fixed end side end and the fixed end side end and another set of the movable end side end adjacent to the circumferential direction opposite to the constant circumferential direction, or the inner The vibration generating device is provided between the peripheral ring portion and the arm portion and attached to the main spring.
　請求項２記載の発明は、前記主バネの損失係数より前記組合せバネの損失係数が大きくされてなる請求項１に記載の振動発生装置である。 The invention according to claim 2 is the vibration generator according to claim 1, wherein the loss coefficient of the combination spring is larger than the loss coefficient of the main spring.
　請求項３記載の発明は、前記主バネのバネ定数より前記組合せバネのバネ定数が大きくされてなる請求項１又は請求項２に記載の振動発生装置である。 The invention according to claim 3 is the vibration generating device according to claim 1 or 2, wherein a spring constant of the combination spring is made larger than a spring constant of the main spring.
　請求項４記載の発明は、前記主バネが金属板により構成され、前記補助バネが高分子材料により構成されてなる請求項１から請求項３のうちいずれか一に記載の振動発生装置である。 The invention according to claim 4 is the vibration generator according to any one of claims 1 to 3, wherein the main spring is made of a metal plate and the auxiliary spring is made of a polymer material. .
　本発明によれば、主バネの固定部が外周リング部及び内周リング部により構成され、主バネの弾性変形部が固定端側端部、アーム部及び可動端側端部により構成されており、補助バネを固定端側端部とこれに隣接する可動端側端部との間に架けるため、比較的小片の補助バネで簡便に構成できる。また、そのような比較的小片の材料によって、変位の大きい固定端側端部と可動端側端部との間にアーム部と並列に補助バネを付設することができる。
　変位の大きい固定端側端部と可動端側端部との間にアーム部と並列に補助バネを付設することができるので、効果的に組合せバネ全体の損失係数（従って減衰率）を増大したり、効果的に組合せバネ全体のバネ定数を増大したりすることができる。
　減衰率やバネ定数の増大により、広帯域に亘って周波数に依る変化の少ない周波数特性への改善（周波数特性曲線の平坦化）が図られ、かかる改善により振動発生装置の広帯域での実用度を向上することができる。
　外周リング部と内周リング部との間隔内に比較的小片の補助バネを主バネに対して並列的に付設することにより、外周リング部と筐体との固定及び内周リング部とヨーク外周部との固定に干渉することなく、かつ、径方向への要スペースの増大による大型化を来たすことなく好個の特性の組合せバネを構成することができる。
　また、補助バネを用いず主バネだけ用いた振動発生装置も得ることができる状況を壊さずに、主バネに補助バネを付設することによって、さらには補助バネの材料を選択することによって、製造性良好に多様な特性の組合せバネを備えた振動発生装置を得ることができる。
　以上説明したように本発明によれば、小型薄型化、製作の容易に適し、バネと可動子とで構成される振動系の周波数特性を容易に変更でき、従って容易に特性改善や用途に応じた特性選択が可能な組合せバネを有した振動発生装置が得られるという効果がある。 According to the present invention, the fixed part of the main spring is constituted by the outer ring part and the inner ring part, and the elastic deformation part of the main spring is constituted by the fixed end side end part, the arm part and the movable end side end part. Since the auxiliary spring is hung between the fixed end side end portion and the movable end side end portion adjacent thereto, the auxiliary spring can be configured simply with a relatively small piece of auxiliary spring. Further, with such a relatively small piece of material, an auxiliary spring can be provided in parallel with the arm portion between the fixed end side end portion and the movable end side end portion having a large displacement.
Since an auxiliary spring can be attached in parallel with the arm part between the fixed end side end part and the movable end side end part with large displacement, the loss coefficient (and hence the damping factor) of the entire combined spring is effectively increased. Or the spring constant of the entire combination spring can be effectively increased.
By increasing the damping factor and spring constant, the frequency characteristics with little frequency change over a wide band can be improved (flattening the frequency characteristic curve), and this improvement improves the practicality of the vibration generator in the wide band. can do.
A relatively small piece of auxiliary spring is attached in parallel to the main spring within the interval between the outer ring part and the inner ring part, thereby fixing the outer ring part and the housing and the inner ring part and the outer circumference of the yoke. It is possible to construct a combination spring having favorable characteristics without interfering with the fixing with the portion and without increasing the size due to an increase in the space required in the radial direction.
In addition, it can be manufactured by attaching an auxiliary spring to the main spring and further selecting the material of the auxiliary spring without breaking the situation where a vibration generator using only the main spring can be obtained without using the auxiliary spring. It is possible to obtain a vibration generator having a combination spring with various characteristics with good characteristics.
As described above, according to the present invention, the frequency characteristics of the vibration system composed of the spring and the mover can be easily changed according to the present invention. There is an effect that a vibration generating device having a combination spring capable of selecting the characteristics can be obtained.
本発明の一実施形態に係る振動発生装置の斜視図である。It is a perspective view of a vibration generator concerning one embodiment of the present invention. 本発明の一実施形態に係る振動発生装置の分解斜視図である。It is a disassembled perspective view of the vibration generator which concerns on one Embodiment of this invention. 本発明の一実施形態に係る振動発生装置に用いられる主バネの平面図である。It is a top view of the main spring used for the vibration generator which concerns on one Embodiment of this invention. 本発明の一実施形態に係る振動発生装置に用いられる主バネの平面図である。補助バネの外形を破線により示す。It is a top view of the main spring used for the vibration generator which concerns on one Embodiment of this invention. The outline of the auxiliary spring is indicated by a broken line. 本発明の一実施形態に係る振動発生装置の垂直断面図である。It is a vertical sectional view of a vibration generator concerning one embodiment of the present invention. 本発明の実施例１，２に係る主バネ、補助バネ及び組合せバネの各バネ定数、主バネ及び組合せバネの各損失係数を記載した表である。It is the table | surface which described each spring constant of the main spring which concerns on Example 1, 2 of this invention, an auxiliary spring, and a combination spring, and each loss coefficient of a main spring and a combination spring. Ｑ値（尖鋭度）の定義式である。It is a definition formula of Q value (sharpness). Ｑ値（尖鋭度）の定義式の補足説明図である。It is supplementary explanatory drawing of the definition formula of Q value (sharpness). 本発明の実施例１に係る可動子の変位ゲイン〔ｍｍ/Ｖ〕の周波数特性図である。It is a frequency characteristic figure of displacement gain [mm / V] of the needle | mover which concerns on Example 1 of this invention. 本発明の実施例１に係る可動子の振動力〔Ｎ〕の周波数特性図である。It is a frequency characteristic figure of the vibration force [N] of the needle | mover which concerns on Example 1 of this invention. 本発明の実施例１に係る可動子の変位〔ｍｍ〕の周波数特性図である。It is a frequency characteristic figure of displacement [mm] of a needle concerning Example 1 of the present invention. 本発明の実施例２に係る可動子の変位ゲイン〔ｍｍ/Ｖ〕の周波数特性図である。It is a frequency characteristic figure of the displacement gain [mm / V] of the needle | mover which concerns on Example 2 of this invention. 本発明の実施例２に係る可動子の振動力〔Ｎ〕の周波数特性図である。It is a frequency characteristic figure of the vibration force [N] of the needle | mover which concerns on Example 2 of this invention. 本発明の実施例２に係る可動子の変位〔ｍｍ〕の周波数特性図である。It is a frequency characteristic figure of the displacement [mm] of the needle | mover which concerns on Example 2 of this invention. 本発明の実施例１に係る可動子の音圧レベル（ＳＰＬ）〔dbSPL〕の周波数特性図である。It is a frequency characteristic figure of the sound pressure level (SPL) [dbSPL] of the needle | mover which concerns on Example 1 of this invention. 本発明の活用例に係る移動通信機器の斜視図である。It is a perspective view of the mobile communication apparatus which concerns on the utilization example of this invention. 本発明の活用例に係るアミューズメント機器の斜視図である。It is a perspective view of the amusement device concerning the example of use of the present invention. 本発明の活用例に係るタッチパネル式情報入力装置の斜視図である。It is a perspective view of the touchscreen type information input device which concerns on the utilization example of this invention. 本発明の活用例に係る音声出力装置の斜視図である。It is a perspective view of the audio | voice output apparatus which concerns on the utilization example of this invention. 従来例に係る可動子の振動力〔Ｎ〕の周波数特性図である。It is a frequency characteristic figure of the vibration force [N] of the needle | mover which concerns on a prior art example.
　以下に本発明の一実施形態につき図面を参照して説明する。以下は本発明の一実施形態であって本発明を限定するものではない。図１は、本発明の一実施形態に係る振動発生装置の斜視図である。図２は、本発明の一実施形態に係る振動発生装置の分解斜視図である。図３、図４は、本発明の一実施形態に係る振動発生装置に用いられる主バネの平面図である。図５は、本発明の一実施形態に係る振動発生装置の垂直断面図である。
　図１及び図２に示すように、本実施形態の振動発生装置１は、ベース筐体２と、コイル３と、センターヨーク４と、マグネット５と、主バネ６と、アウターヨーク７と、上部外周筐体８ａと、下部外周筐体８ｂと、補助バネ９とを備える。センターヨーク４と、マグネット５と、アウターヨーク７とで可動子が構成される。主バネ６と補助バネ９とで組合せバネが構成される。主バネ６は金属板により構成され、補助バネ９は高分子材料により構成される。
　コイル３は固定子に構成される。コイル３は、ベース筐体２の円形板部材２ａの中央に固定される。円形板部材２ａが振動板となるように、円形板部材２ａを筐体本体に対して可動支持しても良い。この場合、コイル３は前述した第２可動子となる。 An embodiment of the present invention will be described below with reference to the drawings. The following is one embodiment of the present invention and does not limit the present invention. FIG. 1 is a perspective view of a vibration generator according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of the vibration generator according to the embodiment of the present invention. 3 and 4 are plan views of the main spring used in the vibration generator according to the embodiment of the present invention. FIG. 5 is a vertical cross-sectional view of a vibration generating apparatus according to an embodiment of the present invention.
As shown in FIGS. 1 and 2, the vibration generator 1 according to the present embodiment includes a base housing 2, a coil 3, a center yoke 4, a magnet 5, a main spring 6, an outer yoke 7, and an upper portion. An outer peripheral housing 8a, a lower outer peripheral housing 8b, and an auxiliary spring 9 are provided. The center yoke 4, the magnet 5, and the outer yoke 7 constitute a mover. The main spring 6 and the auxiliary spring 9 constitute a combination spring. The main spring 6 is made of a metal plate, and the auxiliary spring 9 is made of a polymer material.
The coil 3 is configured as a stator. The coil 3 is fixed to the center of the circular plate member 2 a of the base housing 2. The circular plate member 2a may be movably supported with respect to the casing body so that the circular plate member 2a becomes a diaphragm. In this case, the coil 3 serves as the second movable element described above.
　図２及び図５に示すように、各部は円形に形成されているとともに、コイル３の中心軸Ｃを中心に同心状に配置される。中心軸Ｃに沿ってコイル３が固定される一端側を矢印Ａにより、他端側を矢印Ｂにより示した。
　センターヨーク４と、マグネット５と、アウターヨーク７とからなる可動子は、コイル３に対してその他端側（Ｂ側）から臨むように配置される。主バネ６は、かかる可動子を中心軸Ｃ方向に振動可能に弾性支持する。 As shown in FIGS. 2 and 5, each part is formed in a circular shape and is arranged concentrically around the central axis C of the coil 3. One end side where the coil 3 is fixed along the central axis C is indicated by an arrow A, and the other end side is indicated by an arrow B.
The mover composed of the center yoke 4, the magnet 5, and the outer yoke 7 is disposed so as to face the coil 3 from the other end side (B side). The main spring 6 elastically supports the movable element so as to vibrate in the direction of the central axis C.
　センターヨーク４及びマグネット５は、コイル３の内径より小さく、かつ、互いに略同一径の円盤又は円柱状に形成されている。アウターヨーク７の中央部７ａは、コイル３の外径より大きい円盤状に形成されている。マグネット５の一端側と他端側とは反対磁極を構成する。マグネット５の一端側（Ａ側）にセンターヨーク４が接合する。マグネット５の他端側（Ｂ側）にアウターヨーク７の中央部７ａが接合する。 The center yoke 4 and the magnet 5 are smaller than the inner diameter of the coil 3 and are formed in a disk or a column shape having substantially the same diameter. The central portion 7 a of the outer yoke 7 is formed in a disk shape larger than the outer diameter of the coil 3. One end side and the other end side of the magnet 5 constitute opposite magnetic poles. The center yoke 4 is joined to one end side (A side) of the magnet 5. The central portion 7 a of the outer yoke 7 is joined to the other end side (B side) of the magnet 5.
　アウターヨーク７は、中央部７ａに連続してヨーク外周部７ｂを構成している。ヨーク外周部７ｂは、一端側（Ａ側）において中央部７ａ対して隆起し、他端側（Ｂ側）において中央部７ａ対して同一面に形成されており、従って、ヨーク外周部７ｂは中央部７ａより中心軸方向の寸法が大きくなっている。
　センターヨーク４は、コイル３の径方向の内側に配置される。一方、ヨーク外周部７ｂは、コイル３の径方向の外側に配置される。 The outer yoke 7 constitutes a yoke outer peripheral portion 7b continuous with the central portion 7a. The yoke outer peripheral portion 7b protrudes from the central portion 7a at one end side (A side) and is formed on the same surface as the central portion 7a at the other end side (B side). The dimension in the central axis direction is larger than that of the portion 7a.
The center yoke 4 is disposed inside the coil 3 in the radial direction. On the other hand, the yoke outer peripheral portion 7 b is disposed outside the coil 3 in the radial direction.
　主バネ６は、コイル３の径方向の外側に配置され、該径方向に延在する。
　上部外周筐体８ａと、下部外周筐体８ｂとは、同径の円筒状で上下に連接され、両者の間に主バネ６の外周リング部６ａを挟んで筐体に固定する。
　ヨーク外周部７ｂの一端側（Ａ側）の端面に、外周側が切り欠かれた段差が形成され、その段差を埋めるように主バネ６の内周リング部６ｂが配置されて、内周リング部６ｂがヨーク外周部７ｂに固定される。 The main spring 6 is disposed outside the coil 3 in the radial direction, and extends in the radial direction.
The upper outer casing 8a and the lower outer casing 8b are connected to each other in a cylindrical shape having the same diameter, and are fixed to the casing with an outer peripheral ring portion 6a of the main spring 6 interposed therebetween.
On the end face on one end side (A side) of the yoke outer peripheral portion 7b, a step is formed by cutting out the outer peripheral side, and the inner peripheral ring portion 6b of the main spring 6 is disposed so as to fill the step, and the inner peripheral ring portion 6b is fixed to the yoke outer peripheral portion 7b.
　図３に示すように、主バネ６は、外周リング部６ａ及び内周リング部６ｂがそれぞれリング状に形成され径方向に間隔を隔てて配置されたリング状の板バネである。すなわち、外周リング部６ａの内径が内周リング部６ｂの外径より大きくされることによって、両者は径方向に間隔を隔てている。その間隔に、固定端側端部６ｄ、アーム部６ｃ及び可動端側端部６ｅにより構成される弾性変形部を配置し、外周リング部６ａと内周リング部６ｂとを繋いでいる。 As shown in FIG. 3, the main spring 6 is a ring-shaped leaf spring in which an outer peripheral ring portion 6a and an inner peripheral ring portion 6b are each formed in a ring shape and are arranged at intervals in the radial direction. That is, when the inner diameter of the outer ring part 6a is made larger than the outer diameter of the inner ring part 6b, the two are spaced apart in the radial direction. An elastic deformation portion constituted by the fixed end side end portion 6d, the arm portion 6c and the movable end side end portion 6e is disposed at the interval, and the outer peripheral ring portion 6a and the inner peripheral ring portion 6b are connected.
　固定端側端部６ｄは、外周リング部６ａの内周から径方向内側に突出形成されている。可動端側端部６ｅは、内周リング部６ｂの外周から径方向外側に突出形成されている。
　アーム部６ｃは、固定端側端部６ｄから中心軸Ｃ周りの一定の周方向（図３及び図４において反時計回り方向）に延出し可動端側端部６ｅに繋がる。
　固定端側端部６ｄの突出幅６ｆは、アーム部６ｃの幅６ｇより大きい。可動端側端部６ｅの突出幅６ｈは、アーム部６ｃの幅６ｇより大きく、固定端側端部６ｄの突出幅６ｆより小さい。 The fixed end 6d is formed so as to protrude radially inward from the inner periphery of the outer ring portion 6a. The movable end side end portion 6e is formed to protrude radially outward from the outer periphery of the inner peripheral ring portion 6b.
The arm portion 6c extends from the fixed end side end portion 6d in a constant circumferential direction around the central axis C (counterclockwise direction in FIGS. 3 and 4) and is connected to the movable end side end portion 6e.
The protruding width 6f of the fixed end 6d is larger than the width 6g of the arm 6c. The protrusion width 6h of the movable end side end portion 6e is larger than the width 6g of the arm portion 6c and smaller than the protrusion width 6f of the fixed end side end portion 6d.
　バネ鋼板に３つの同形状のスパイラル溝６ｋを順次１２０度ずらした配置で打ち抜くことによって、以上のような構成を各１２０度ずつの領域に構成している。スパイラル溝６ｋは、均一で狭小な溝幅で構成されている。スパイラル溝６ｋは、異なる半径位置で周方向にそれぞれ延在する外周溝６ｋ－１，内周溝６ｋ－２と、これらの端部同士を繋ぎ径方向に延在する径溝６ｋ－３により構成される。径溝６ｋ－３の外端に連続して外周溝６ｋ－１が周方向に延びている。径溝６ｋ－３の内端に連続して内周溝６ｋ－２が周方向に延びている。
　このような主バネ６によれば、外周リング部６ａと内周リング部６ｂとの距離が短い、コンパクトなリング状板バネを構成することができる。
　主バネ６は、１つの固定端側端部６ｄ、これに連続する１つのアーム部６ｃ及びこれに連続する１つの可動端側端部６ｅとからなる組を、一周を３つに分割してできる異なる１２０度ずつ角度領域に１組ずつ配して内周リング部６ｂを３アームで支持する。
　３アームでなく、４アーム以上としてもよい。３アーム以上とするのは、可動子の振動軸がぶれないように安定的に支持するためである。 By punching out three spiral grooves 6k having the same shape in the spring steel plate in an arrangement shifted sequentially by 120 degrees, the above-described configuration is configured in a region of 120 degrees each. The spiral groove 6k has a uniform and narrow groove width. The spiral groove 6k includes an outer peripheral groove 6k-1 and an inner peripheral groove 6k-2 that extend in the circumferential direction at different radial positions, and a radial groove 6k-3 that connects these ends and extends in the radial direction. Is done. An outer peripheral groove 6k-1 extends in the circumferential direction continuously to the outer end of the radial groove 6k-3. An inner circumferential groove 6k-2 extends in the circumferential direction continuously to the inner end of the radial groove 6k-3.
According to such a main spring 6, a compact ring-shaped leaf spring in which the distance between the outer ring portion 6a and the inner ring portion 6b is short can be configured.
The main spring 6 is formed by dividing a set of one fixed end side end portion 6d, one arm portion 6c continuous therewith and one movable end side end portion 6e continuous thereto into three portions. The inner ring portion 6b is supported by the three arms by arranging one set in the angular region by 120 degrees which can be different.
It is good also as 4 arms or more instead of 3 arms. The reason for using three or more arms is to stably support the vibration axis of the mover so that it does not shake.
　図４に３つの補助バネ９，９，９の外形を破線により示した。図４に示すように、３つの補助バネ９，９，９がそれぞれ、固定端側端部６ｄと、当該固定端側端部６ｄと前記一定の周方向と逆の周方向（図３及び図４において時計回り方向）に隣接する他の組の可動端側端部６ｅとの間に架けられ主バネ６に付設されている。補助バネ９の両端は、固定端側端部６ｄと可動端側端部６ｅとに貼付されて固定される。
　なお、図４に示すＤ－Ｄ線に沿って切った主バネ６と補助バネ９とからなる組合せバネの断面が図５に示される。
　本振動発生装置１は、以上説明した構成を有し、コイル３に駆動電力が入力されると、センターヨーク４、マグネット５及びアウターヨーク７からなる可動子が、中心軸Ｃ方向に振動する。 In FIG. 4, the external shapes of the three auxiliary springs 9, 9, 9 are indicated by broken lines. As shown in FIG. 4, each of the three auxiliary springs 9, 9, 9 has a fixed end side end portion 6d and a circumferential direction opposite to the fixed end side end portion 6d (see FIGS. 3 and 5). 4 is attached to the main spring 6 between the other end 6e of the movable end side adjacent in the clockwise direction (4). Both ends of the auxiliary spring 9 are affixed and fixed to the fixed end side end 6d and the movable end side end 6e.
FIG. 5 shows a cross section of the combined spring composed of the main spring 6 and the auxiliary spring 9 cut along the line DD shown in FIG.
The vibration generator 1 has the above-described configuration, and when driving power is input to the coil 3, the mover including the center yoke 4, the magnet 5, and the outer yoke 7 vibrates in the direction of the central axis C.
　以上のような本実施形態の振動発生装置１によれば、小型薄型化、製作の容易に適し、バネと可動子とで構成される振動系の周波数特性を容易に変更でき、従って容易に特性改善や用途に応じた特性選択が可能な組合せバネを有した振動発生装置が得られるという効果がある。
　補助バネの付加により組合せバネの減衰率やバネ定数を増大させ、広帯域に亘って周波数に依る変化の少ない周波数特性への改善（周波数特性曲線の平坦化）を図り、かかる改善により振動発生装置の広帯域での実用度を向上することができる。そのような実施例１，２及び活用例を以下に示す。 According to the vibration generator 1 of the present embodiment as described above, the frequency characteristics of the vibration system composed of the spring and the mover can be easily changed, and thus the characteristics can be easily changed. There is an effect that a vibration generating apparatus having a combination spring that can be improved or selected according to application can be obtained.
By adding an auxiliary spring, the damping rate and spring constant of the combined spring are increased, and the frequency characteristics with little frequency variation over a wide band are improved (frequency characteristic curve is flattened). The practicality in a wide band can be improved. Examples 1 and 2 and examples of use are shown below.
　図６は、実施例１，２に係る主バネ、補助バネ及び組合せバネの各バネ定数、主バネ及び組合せバネの各損失係数を記載した表である。
　その他の条件としては、実施例１は外径φ６０〔ｍｍ〕、共振周波数３７．２〔Ｈｚ〕であり、実施例２は外径φ２４〔ｍｍ〕、共振周波数５２〔Ｈｚ〕であり、実施例１，２ともに上記実施形態に従うものである。
　また、補助バネには、不織布の基材にアクリル系樹脂を主成分とする粘着剤を塗布して作成したテープを使用した。
　図６の表からわかるように、主バネに補助バネを付設することによって、バネ定数、損失係数ともに増大している。 FIG. 6 is a table in which the spring constants of the main spring, the auxiliary spring, and the combination spring according to Examples 1 and 2 and the loss coefficients of the main spring and the combination spring are described.
As other conditions, Example 1 has an outer diameter of φ60 [mm] and a resonance frequency of 37.2 [Hz], and Example 2 has an outer diameter of φ24 [mm] and a resonance frequency of 52 [Hz]. Both 1 and 2 follow the above embodiment.
Moreover, the auxiliary spring used the tape created by apply | coating the adhesive which has an acrylic resin as a main component to the base material of a nonwoven fabric.
As can be seen from the table in FIG. 6, both the spring constant and the loss factor are increased by attaching the auxiliary spring to the main spring.
　周波数特性を評価するため、図７Ａに、Ｑ値の定義を示した。Ｑ値は共振の鋭さを表す値で尖鋭度ともいう。
　図７Ａに示したＱ値の定義式の第１項と第２項の関係でわかるように、Ｑ値と損失係数ηは反比例の関係にある。この関係性と図６の表を併せ見ればわかるように、実施例１，２ともに損失係数ηが増大したことによって、Ｑ値を小さく、すなわち、共振のピークを抑えることができることとなる。 In order to evaluate the frequency characteristics, FIG. 7A shows the definition of the Q value. The Q value is a value representing the sharpness of resonance and is also called sharpness.
As can be seen from the relationship between the first term and the second term of the Q value defining equation shown in FIG. As can be seen from a combination of this relationship and the table of FIG. 6, the increase in the loss factor η in both Examples 1 and 2 can reduce the Q value, that is, suppress the resonance peak.
　図８は実施例１に係る可動子の変位ゲイン〔ｍｍ/Ｖ〕の周波数特性図、図９は実施例１に係る可動子の振動力〔Ｎ〕の周波数特性図、図１０は実施例１に係る可動子の変位〔ｍｍ〕の周波数特性図である。
　図１１は実施例２に係る可動子の変位ゲイン〔ｍｍ/Ｖ〕の周波数特性図、図１２は実施例２に係る可動子の振動力〔Ｎ〕の周波数特性図、図１３は実施例２に係る可動子の変位〔ｍｍ〕の周波数特性図である。
　図８～図１３において、破線曲線は比較のための従来例である。図８～図１０における従来例は実施例１の構成に対し補助バネを除いたものとし、その他は実施例１と同構成である。図１１～図１３における従来例は実施例２の構成に対し補助バネを除いたものとし、その他は実施例２と同構成である。したがって、各従来例に適用されるバネ全体は、図６の表に示した主バネの特性を有する。なお、本発明の実施例１，２の方がバネ定数が大きいため、図１０及び図１３に示すように従来例と同程度の最大振幅となるように、本発明の実施例１，２のコイルに入力する駆動電力を従来例のそれより大きくしている。 8 is a frequency characteristic diagram of the displacement gain [mm / V] of the mover according to the first embodiment, FIG. 9 is a frequency characteristic diagram of the vibration force [N] of the mover according to the first embodiment, and FIG. It is a frequency characteristic figure of displacement [mm] of a needle concerning concerning.
11 is a frequency characteristic diagram of the displacement gain [mm / V] of the mover according to the second embodiment, FIG. 12 is a frequency characteristic diagram of the vibration force [N] of the mover according to the second embodiment, and FIG. It is a frequency characteristic figure of displacement [mm] of a needle concerning concerning.
8 to 13, the broken line curve is a conventional example for comparison. 8 to 10 are the same as those of the first embodiment except that the auxiliary spring is removed from the configuration of the first embodiment. 11 to 13 are the same as those of the second embodiment except that the auxiliary spring is removed from the configuration of the second embodiment. Therefore, the whole spring applied to each conventional example has the characteristics of the main spring shown in the table of FIG. Since the first and second embodiments of the present invention have a larger spring constant, as shown in FIGS. 10 and 13, the first and second embodiments of the present invention have the same maximum amplitude as the conventional example. The driving power input to the coil is made larger than that of the conventional example.
　図８に示すように実施例１にあっては、最大ゲインＧｍａｘをＤＣゲインＧ１の２．３倍程度と、従来例に比較しても大きく抑えている。
　図９に示すように実施例１にあっては従来例に比較して、特性曲線の裾野が広がり（すなわち、ピークからの傾斜ラインが緩やかになり）、共振周波数に対する高帯域及び低帯域の双方において、振動力が向上している。
　図１０に示すように実施例１にあっては従来例に比較して、特に共振周波数に対する低帯域において振幅変位量が向上している。 As shown in FIG. 8, in the first embodiment, the maximum gain Gmax is about 2.3 times the DC gain G1, which is greatly suppressed as compared with the conventional example.
As shown in FIG. 9, in the first embodiment, the base of the characteristic curve is broader (that is, the inclined line from the peak becomes gentler) than in the conventional example, and both the high band and the low band with respect to the resonance frequency. The vibration force is improved.
As shown in FIG. 10, in the first embodiment, the amplitude displacement is improved particularly in the low band with respect to the resonance frequency as compared with the conventional example.
　図１１に示すように実施例２にあっては、最大ゲインＧｍａｘをＤＣゲインＧ１の１．４倍程度と、従来例に比較しても大きく抑えている。
　図１２に示すように実施例２にあっては従来例に比較して、特性曲線の裾野広がり（すなわち、ピークからの傾斜ラインが緩やかになり）、共振周波数に対する高帯域及び低帯域の双方において、振動力が向上している。
　図１０に示すように実施例１にあっては従来例に比較して、特に共振周波数に対する低帯域において振幅変位量が向上している。 As shown in FIG. 11, in the second embodiment, the maximum gain Gmax is about 1.4 times the DC gain G1, which is much smaller than the conventional example.
As shown in FIG. 12, in the second embodiment, compared with the conventional example, the base of the characteristic curve is broadened (that is, the inclined line from the peak becomes gentle), both in the high band and the low band with respect to the resonance frequency. The vibration force is improved.
As shown in FIG. 10, in the first embodiment, the amplitude displacement is improved particularly in the low band with respect to the resonance frequency as compared with the conventional example.
　図８～図１３からわかるように実施例１，２のいずれにおいても各３つの周波数特性のＱ値は小さくなり、周波数特性曲線の平坦化が図られている。
　このように、周波数特性曲線の平坦化が図られる、すなわち、広帯域に亘って周波数に依る変化の少ない周波数特性への改善が図られることにより、振動発生装置の広帯域での実用度が広がる。
　実施例１，２で示されるように、本発明では最大振幅を抑えることができるため、部品同士の干渉が生じない程度まで入力電圧を上げることができる。すなわち、可動子の許容可動範囲が同じであっても、本発明によれば従来よりも入力電圧を上げることができ、その結果、従来よりも広帯域で大きな振動力を得ることが可能となる。
　したがって、専ら共振周波数付近での使用に限定されていた従来の振動発生装置に対し、広帯域での使用が可能となる。共振周波数に対する高帯域及び低帯域における出力の低下が改善される。
　広帯域での使用が可能となるので、音声出力を含め振動による表現力が向上する。
　音声出力装置を構成するにあたっては、上述したベース筐体２の底面をボードやパネル（本振動発生装置が搭載される親機器の筐体等を含む）に付けて本振動発生装置の発生振動を当該ボードやパネルに伝えることによって、当該ボードやパネルを振動板とした音声出力装置を構成することができる。従来に比較して高音域でも低音域でも大きな音出力を得ることができ、低音出力から高音出力まで利用性が広がる。 As can be seen from FIGS. 8 to 13, the Q values of the three frequency characteristics are small in both the first and second embodiments, and the frequency characteristic curve is flattened.
As described above, the frequency characteristic curve is flattened, that is, the frequency characteristic with little change depending on the frequency over a wide band is improved, so that the practicality of the vibration generator in the wide band is widened.
As shown in the first and second embodiments, the maximum amplitude can be suppressed in the present invention, so that the input voltage can be increased to such an extent that interference between components does not occur. That is, even if the allowable movable range of the mover is the same, according to the present invention, it is possible to increase the input voltage as compared with the conventional case, and as a result, it is possible to obtain a large vibration force in a wider band than the conventional case.
Therefore, it is possible to use the conventional vibration generator limited to use in the vicinity of the resonance frequency in a wide band. The output drop in the high band and the low band with respect to the resonance frequency is improved.
Since it can be used in a wide band, the expressive power by vibration including voice output is improved.
In constructing the audio output device, the bottom of the base housing 2 described above is attached to a board or panel (including the housing of the parent device on which the vibration generating device is mounted) to generate the vibration generated by the vibration generating device. By transmitting the information to the board or panel, an audio output device using the board or panel as a diaphragm can be configured. Compared to the prior art, it is possible to obtain a large sound output in both the high and low sound ranges, and the utility expands from the low sound output to the high sound output.
　図１４は、実施例１に係る可動子の音圧レベル（ＳＰＬ）〔dbSPL〕の周波数特性図である。図１４からわかるように、実施例１では、［1/(2*π)］*√（K/m）で表される共振周波数を約４０〔Hz〕に設定したことにより、１００〔Hz〕より低域～１万〔Hz〕超まで広帯域での音声出力が可能となった。このように、所望の周波数帯域の最低値又は最低値より低い周波数を共振周波数とする振動発生装置を用いることにより、所望の周波数帯域での音声出力が可能となる。 FIG. 14 is a frequency characteristic diagram of the sound pressure level (SPL) [dbSPL] of the mover according to the first embodiment. As can be seen from FIG. 14, in the first embodiment, the resonance frequency represented by [1 / (2 * π)] * √ (K / m) is set to about 40 [Hz]. It has become possible to output audio in a wide band from lower to over 10,000 [Hz]. As described above, by using the vibration generator that uses the lowest frequency in the desired frequency band or a frequency lower than the lowest value as the resonance frequency, it is possible to output sound in the desired frequency band.
　図１５Ａ～Ｄに本発明の振動発生装置の活用例を示す。図１５Ａは、本実施形態の振動発生装置１を搭載した一例の移動通信機器１１の斜視図である。本振動発生装置１のベース筐体２の底面が移動通信機器１１の筐体に固定されている。本振動発生装置１によれば、広帯域で駆動され広帯域の振動を出力することができるので、振動表現力が向上し、例えば使用者一人一人が最も感じ易い帯域の呼び出し振動を選択することができるなど、使用者の好みに応じた帯域の呼び出し振動を発生させることができる。 15A to 15D show examples of using the vibration generator of the present invention. FIG. 15A is a perspective view of an example mobile communication device 11 equipped with the vibration generator 1 of the present embodiment. The bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing of the mobile communication device 11. According to this vibration generator 1, since it is driven in a wide band and can output a wide-band vibration, the vibration expressing power is improved, and for example, it is possible to select a ringing vibration in a band that is most easily felt by each user. For example, it is possible to generate a ringing vibration in a band according to the user's preference.
　図１５Ｂは、本実施形態の振動発生装置１を搭載した一例のアミューズメント機器１２の斜視図である。本振動発生装置１のベース筐体２の底面がアミューズメント機器１２の握り部で筐体に固定されている。本振動発生装置１によれば、広帯域で駆動され広帯域の振動を出力することができるので、振動表現力が向上し、例えばシューティングゲームで大きな銃で撃った感覚と小さな銃で撃った感覚の違いを振動周波数を変更することで表現することができるなど、より現実的なゲームの臨場感を使用者に与えることができる。　　 FIG. 15B is a perspective view of an example amusement device 12 equipped with the vibration generator 1 of the present embodiment. The bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing by a grip portion of the amusement device 12. According to this vibration generator 1, since it is driven in a wide band and can output a wide-band vibration, the vibration expressive power is improved. For example, a difference between a feeling of shooting with a large gun and a feeling of shooting with a small gun in a shooting game Can be expressed by changing the vibration frequency, so that the user can have a more realistic game experience. *
　図１５Ｃは、本実施形態の振動発生装置１を搭載した一例のタッチパネル式情報入力装置１３の斜視図である。本振動発生装置１のベース筐体２の底面がタッチパネル式情報入力装置１３の操作部裏面で筐体に固定されている。タッチパネル式情報入力装置１３は、操作ボタンは映像であるため機械的操作ボタンのような操作感触が得られない。しかし、本振動発生装置１によれば、広帯域で駆動され広帯域の振動を出力することができるので、振動表現力が向上し、例えば操作ボタン映像を押した時に、機械的操作ボタンのような操作感触を表現することができるなど、様々な感触をより現実的に表現することができる。 FIG. 15C is a perspective view of an example touch panel type information input device 13 equipped with the vibration generator 1 of the present embodiment. The bottom surface of the base housing 2 of the vibration generator 1 is fixed to the housing on the back of the operation unit of the touch panel type information input device 13. In the touch panel type information input device 13, since the operation buttons are images, an operation feeling like a mechanical operation button cannot be obtained. However, according to the vibration generating device 1, since it is driven in a wide band and can output a wide-band vibration, the vibration expressing power is improved. For example, when an operation button image is pressed, an operation like a mechanical operation button is performed. Various feelings can be expressed more realistically, such as being able to express a feeling.
　図１５Ｄは、本実施形態の振動発生装置１を搭載した一例の音声出力装置１４の斜視図である。本振動発生装置１のベース筐体２の底面が音声出力装置１４のパネル背面に固定されている。本振動発生装置１によれば、広帯域で駆動され広帯域の振動を出力することができるので、音声信号を入力することにより、入力した音声信号の周波数振動を発生させることができる。したがって、本振動発生装置１をあらゆる機器のパネルや筐体等に取り付けることによって、本振動発生装置１を音声発生源とし、取り付けられたパネルや筐体等を振動板とした音声出力装置（音声出力機能付き機器）を構成することができる。 FIG. 15D is a perspective view of an example audio output device 14 equipped with the vibration generator 1 of the present embodiment. The bottom surface of the base housing 2 of the vibration generator 1 is fixed to the panel back surface of the audio output device 14. According to this vibration generator 1, since it can be driven in a wide band and can output a wide band vibration, it is possible to generate a frequency vibration of the input audio signal by inputting the audio signal. Therefore, by attaching the vibration generating device 1 to a panel or casing of any device, the sound generating device 1 is used as a sound source, and the sound output device (sound (Equipment with output function) can be configured.
　なお、補助バネは、上記実施形態の架設位置に代えて　内周リング部６ｂとアーム部６ｃとの間に架設してもよい。この場合、補助バネの架設位置を周方向に沿って移動することによって、同じ補助バネでもその効き具合を自由に選択することができる。 Note that the auxiliary spring may be installed between the inner ring portion 6b and the arm portion 6c instead of the installation position of the above embodiment. In this case, by moving the construction position of the auxiliary spring along the circumferential direction, the effectiveness of the same auxiliary spring can be freely selected.
　振動や音声の発生装置として利用することができる。例えば、携帯電話などの移動通信機器、ゲーム用コントローラなどのアミューズメント機器、タッチパネル式情報入力装置等に搭載される振動発生装置や、音声出力装置の音声発生源として利用することができる。 It can be used as a vibration or sound generator. For example, it can be used as a sound generation source of a vibration generator mounted on a mobile communication device such as a mobile phone, an amusement device such as a game controller, a touch panel type information input device, or a sound output device.
符号の説明Explanation of symbols
１ 振動発生装置
２ ベース筐体
２ａ 円形板部材
３ コイル
４ センターヨーク
５ マグネット
６ 主バネ
６ａ 外周リング部
６ｂ 内周リング部
６ｃ アーム部
６ｄ 固定端側端部
６ｅ 可動端側端部
７ アウターヨーク
７ｂ ヨーク外周部
８ａ 上部外周筐体
８ｂ 下部外周筐体
９ 補助バネ
Ｃ 中心軸 DESCRIPTION OF SYMBOLS 1 Vibration generator 2 Base housing | casing 2a Circular plate member 3 Coil 4 Center yoke 5 Magnet 6 Main spring 6a Outer ring part 6b Inner ring part 6c Arm part 6d Fixed end side end part 6e Movable end side end part 7 Outer yoke 7b Yoke outer peripheral part 8a Upper outer peripheral casing 8b Lower outer peripheral casing 9 Auxiliary spring C Center axis

Claims (4)

  1. 中心軸方向の一端において振動板その他の部材に固定されたコイルと、前記コイルに対してその他端側から臨み前記中心軸方向に振動するマグネット及びヨークにより構成される可動子と、前記可動子を前記中心軸方向に振動可能に弾性支持する組合せバネと、前記コイル、前記可動子及び前記組合せバネを収める筐体とを備え、
    前記ヨークの一部は前記コイルの径方向の外側に配置されるヨーク外周部を構成し、
    前記組合せバネは、主バネと、補助バネとを有し、
    前記主バネは、前記筐体に対して固定された外周リング部と、前記外周リング部に対して前記径方向内側に間隔を隔てて配置され前記ヨーク外周部に固定された内周リング部と、前記外周リング部の内周から前記径方向内側に突出形成された固定端側端部と、前記内周リング部の外周から前記径方向外側に突出形成された可動端側端部と、前記固定端側端部から前記中心軸周りの一定の周方向に延出し前記可動端側端部に繋がるアーム部とを有し、
    前記主バネは、１つの前記固定端側端部、これに連続する１つの前記アーム部及びこれに連続する１つの前記可動端側端部とからなる組を、一周を３以上に分割してできる異なる角度領域に１組ずつ配して前記内周リング部を３アーム以上で支持し、
    前記補助バネは、前記主バネと異なる材料により構成され、
    前記補助バネが、前記固定端側端部と、当該固定端側端部と前記一定の周方向と逆の周方向に隣接する他の組の前記可動端側端部との間、又は前記内周リング部と前記アーム部との間に架けられ前記主バネに付設されてなる振動発生装置。     A mover comprising a coil fixed to a diaphragm or other member at one end in the central axis direction, a magnet and a yoke that face the coil from the other end side and vibrate in the central axis direction; and A combination spring elastically supported so as to vibrate in the direction of the central axis, and a housing that houses the coil, the mover, and the combination spring;
    A part of the yoke constitutes a yoke outer peripheral portion disposed on the outer side in the radial direction of the coil,
    The combination spring has a main spring and an auxiliary spring,
    The main spring includes an outer peripheral ring portion fixed to the casing, and an inner peripheral ring portion disposed on the radially outer side with respect to the outer peripheral ring portion and fixed to the outer peripheral portion of the yoke. A fixed end side end projecting from the inner periphery of the outer ring portion to the radially inner side, a movable end side end projecting from the outer periphery of the inner ring portion to the radially outer side, An arm portion extending from a fixed end side end portion in a certain circumferential direction around the central axis and connected to the movable end side end portion;
    The main spring is composed of one fixed end side end, one arm part continuous with the fixed end side, and one movable end side end continuous with the arm part. One set is arranged in different angular areas that can be supported and the inner ring part is supported by three or more arms,
    The auxiliary spring is made of a material different from the main spring,
    The auxiliary spring is between the fixed end side end and the fixed end side end and another set of the movable end side end adjacent to the circumferential direction opposite to the constant circumferential direction, or the inner A vibration generator that is provided between the peripheral ring portion and the arm portion and attached to the main spring.
  2. 前記主バネの損失係数より前記組合せバネの損失係数が大きくされてなる請求項１に記載の振動発生装置。 The vibration generating device according to claim 1, wherein a loss coefficient of the combination spring is larger than a loss coefficient of the main spring.
  3. 前記主バネのバネ定数より前記組合せバネのバネ定数が大きくされてなる請求項１又は請求項２に記載の振動発生装置。 The vibration generator according to claim 1 or 2, wherein a spring constant of the combination spring is larger than a spring constant of the main spring.
  4. 前記主バネが金属板により構成され、前記補助バネが高分子材料により構成されてなる請求項１から請求項３のうちいずれか一に記載の振動発生装置。 The vibration generator according to any one of claims 1 to 3, wherein the main spring is made of a metal plate, and the auxiliary spring is made of a polymer material.
PCT/JP2009/051893 2008-02-20 2009-02-04 Vibration generator WO2009104475A1 (en)

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JP5943419B2 (en) * 2012-03-16 2016-07-05 日本電産セイミツ株式会社 Vibration generator

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003080171A (en) * 2001-09-13 2003-03-18 Shicoh Eng Co Ltd Electromagnetic actuator
JP2003163981A (en) * 2001-07-25 2003-06-06 Matsushita Electric Ind Co Ltd Electric/mechanical/acoustic transducer and portable terminal equipment
JP2004195444A (en) * 2002-12-13 2004-07-15 Shicoh Eng Co Ltd Electromagnetic actuator
JP2007275776A (en) * 2006-04-06 2007-10-25 Citizen Electronics Co Ltd Vibrator

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003163981A (en) * 2001-07-25 2003-06-06 Matsushita Electric Ind Co Ltd Electric/mechanical/acoustic transducer and portable terminal equipment
JP2003080171A (en) * 2001-09-13 2003-03-18 Shicoh Eng Co Ltd Electromagnetic actuator
JP2004195444A (en) * 2002-12-13 2004-07-15 Shicoh Eng Co Ltd Electromagnetic actuator
JP2007275776A (en) * 2006-04-06 2007-10-25 Citizen Electronics Co Ltd Vibrator

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