JP6124764B2 - Diaphragm for speaker and speaker - Google Patents
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- JP6124764B2 JP6124764B2 JP2013220152A JP2013220152A JP6124764B2 JP 6124764 B2 JP6124764 B2 JP 6124764B2 JP 2013220152 A JP2013220152 A JP 2013220152A JP 2013220152 A JP2013220152 A JP 2013220152A JP 6124764 B2 JP6124764 B2 JP 6124764B2
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- 239000000463 material Substances 0.000 claims description 40
- 229920005989 resin Polymers 0.000 claims description 29
- 239000011347 resin Substances 0.000 claims description 29
- 230000002093 peripheral effect Effects 0.000 claims description 23
- 238000001746 injection moulding Methods 0.000 claims description 19
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 16
- 239000002041 carbon nanotube Substances 0.000 claims description 16
- 229910021393 carbon nanotube Inorganic materials 0.000 claims description 16
- 229920000049 Carbon (fiber) Polymers 0.000 claims description 8
- 229920000106 Liquid crystal polymer Polymers 0.000 claims description 8
- 239000004977 Liquid-crystal polymers (LCPs) Substances 0.000 claims description 8
- 239000004917 carbon fiber Substances 0.000 claims description 8
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 8
- 125000004122 cyclic group Chemical group 0.000 claims description 6
- 239000000835 fiber Substances 0.000 claims description 6
- 229920005672 polyolefin resin Polymers 0.000 claims description 6
- 230000007423 decrease Effects 0.000 description 12
- 230000000694 effects Effects 0.000 description 9
- 230000000052 comparative effect Effects 0.000 description 7
- 238000002347 injection Methods 0.000 description 7
- 239000007924 injection Substances 0.000 description 7
- 230000008859 change Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000006872 improvement Effects 0.000 description 5
- 239000000126 substance Substances 0.000 description 5
- 238000005452 bending Methods 0.000 description 3
- 239000000470 constituent Substances 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000003014 reinforcing effect Effects 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- -1 cyclic olefin Chemical class 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 229920006351 engineering plastic Polymers 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- JRZJOMJEPLMPRA-UHFFFAOYSA-N olefin Natural products CCCCCCCC=C JRZJOMJEPLMPRA-UHFFFAOYSA-N 0.000 description 2
- 229920000642 polymer Polymers 0.000 description 2
- 238000012935 Averaging Methods 0.000 description 1
- 239000004697 Polyetherimide Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
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- 229920001601 polyetherimide Polymers 0.000 description 1
- 150000003457 sulfones Chemical class 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
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- Diaphragms For Electromechanical Transducers (AREA)
Description
本発明は、スピーカ用の振動板、および、それを備えるスピーカに関するものである。 The present invention relates to a diaphragm for a speaker and a speaker including the diaphragm.
スピーカ用の振動板は、いずれも板状であるため、特定の周波数（分割共振周波数）以上で振動板の分割共振を生じる。この分割共振が発生すると、音圧周波数特性上にピーク・ディップが発生し、音質を著しく悪化させてしまう問題がある。 Since all the diaphragms for a speaker are plate-shaped, the diaphragms generate a resonance at a specific frequency (divided resonance frequency) or higher. When this divided resonance occurs, there is a problem that a peak dip occurs on the sound pressure frequency characteristic and the sound quality is significantly deteriorated.
分割共振の発生を抑制するためには、振動板の分割共振周波数を高くすることが考えられる。振動板の分割共振周波数を高くするためには、振動板の剛性の向上が必要であるが、従来は、振動板の剛性を向上させるために振動板の厚さ増加することが行われていた。しかし、振動板の厚さが増加することにより、振動板の質量が大きくなることで、出力音圧レベルが低下するという問題があった。 In order to suppress the occurrence of split resonance, it is conceivable to increase the split resonance frequency of the diaphragm. In order to increase the divided resonance frequency of the diaphragm, it is necessary to improve the rigidity of the diaphragm. Conventionally, in order to improve the rigidity of the diaphragm, the thickness of the diaphragm has been increased. . However, there is a problem in that the output sound pressure level is lowered due to an increase in the mass of the diaphragm due to an increase in the thickness of the diaphragm.
これに対して、例えば、特許文献１（実開平３−４６２９６号公報）では、ポリアリルサルホンやポリエーテルイミドなどのエンジニアリングプラスチックの射出成型によって、振動板中央から外周部へかけて高さが低くなる補強リブを一体成型し、振動板剛性の向上を図っている。 On the other hand, for example, in Patent Document 1 (Japanese Utility Model Publication No. 3-46296), the height from the center of the diaphragm to the outer peripheral portion is increased by injection molding of engineering plastics such as polyallyl sulfone and polyetherimide. The lower reinforcing ribs are integrally molded to improve diaphragm rigidity.
しかしながら、上記のエンジニアリングプラスチックのヤング率は３ＧＰａ程度であり、アルミなどの金属材料のヤング率の１／１０以下でしかない。したがって、補強リブを取り付けたとしても、十分な剛性増加にはつながらない。また、前記特許文献１に記載のストレートコーンおよびカーブドコーンでは、振動板の外周部が振動するモードが最も音圧周波数特性上のピーク・ディップに影響を与えるため、振動板の中心から外周部へかけて高さが低くなる補強リブでは、特に重要な振動板外周部において十分な剛性を得ることができない。 However, the Young's modulus of the engineering plastic is about 3 GPa, which is only 1/10 or less of the Young's modulus of a metal material such as aluminum. Therefore, even if the reinforcing rib is attached, it does not lead to a sufficient increase in rigidity. Further, in the straight cone and the curved cone described in Patent Document 1, the mode in which the outer peripheral portion of the diaphragm vibrates most affects the peak dip on the sound pressure frequency characteristic, and therefore, from the center of the diaphragm to the outer peripheral portion. With the reinforcing rib whose height decreases over time, sufficient rigidity cannot be obtained at the outer peripheral portion of the diaphragm that is particularly important.
これに対して、特許文献２（特許第５２１４０１６号公報）では、振動板の構成材料として、炭素繊維強化液晶ポリマー、環状オレフィン系樹脂およびカーボンナノチューブを含む材料を用いることで、振動板のヤング率を３０ＧＰａ程度に増加させ、密度（ρ）と弾性率（Ｅ）で定義される音速（音速＝（Ｅ／ρ）０．５）の向上を図っている。特許文献１の材料を用いた振動板では、音速が約１５００ｍ／ｓであるのに対して、特許文献２の材料を用いた振動板では、音速が約５０００ｍ／ｓまで向上する。一般に、音速が大きいほど、スピーカに入力される電力信号に対する振動板の追従性が向上するため、音のひずみが低減される。 On the other hand, in Patent Document 2 (Japanese Patent No. 5214016), the Young's modulus of the diaphragm is obtained by using a material containing a carbon fiber reinforced liquid crystal polymer, a cyclic olefin resin, and carbon nanotubes as a constituent material of the diaphragm. Is increased to about 30 GPa to improve the speed of sound (sound speed = (E / ρ) 0.5 ) defined by density (ρ) and elastic modulus (E). In the diaphragm using the material of Patent Document 1, the speed of sound is about 1500 m / s, whereas in the diaphragm using the material of Patent Document 2, the speed of sound is improved to about 5000 m / s. In general, as the sound speed increases, the followability of the diaphragm with respect to the power signal input to the speaker is improved, so that sound distortion is reduced.
特許文献２に記載の構成材料はカーボンナノチューブを含むため、この材料を用いて射出成型加工によって製造された振動板は、射出方向と、射出方向に略直行する方向とで異方性を持つ。つまり、射出方向は、カーボンナノチューブの繊維方向（長手方向）となるため剛性が高く、射出方向と直交する方向は、カーボンナノチューブの繊維方向と直交する方向となるため剛性が低い。振動板の射出成型は、振動板中央から外周部へかけて半径方向に射出する方法が一般的であるため、得られる振動板は、半径方向の剛性が高く、周方向の剛性が低いものとなる。 Since the constituent material described in Patent Document 2 includes carbon nanotubes, a diaphragm manufactured by injection molding using this material has anisotropy in the injection direction and in a direction substantially perpendicular to the injection direction. That is, since the injection direction is the fiber direction (longitudinal direction) of the carbon nanotubes, the rigidity is high, and the direction orthogonal to the injection direction is a direction orthogonal to the fiber direction of the carbon nanotubes, so the rigidity is low. The injection molding of the diaphragm is generally a method of injecting in the radial direction from the center of the diaphragm to the outer peripheral portion. Therefore, the obtained diaphragm has high radial rigidity and low circumferential rigidity. Become.
射出成型による振動板の製造においては、均質な材料分布および均一な振動板形状が得られるが、このことから、振動板の分割共振状態において、振動板の中心軸を基準とした軸対称の振動モードが生じやすくなる。また、軸対称振動モードは、例えば、振動板の外周部が周方向に同位相で振動するモードなどであり、振動板の周方向の伸びを伴う振動モードであるところ、上述のように特許文献２の振動板は、周方向の剛性が低いという異方性を有しているため、軸対称振動モードはより一層生じやすくなる。 In the production of a diaphragm by injection molding, a uniform material distribution and a uniform diaphragm shape can be obtained. From this, in a split resonance state of the diaphragm, axisymmetric vibration with respect to the central axis of the diaphragm Mode is likely to occur. The axially symmetric vibration mode is, for example, a mode in which the outer peripheral portion of the diaphragm vibrates in the same phase in the circumferential direction, and is a vibration mode accompanied by the extension of the diaphragm in the circumferential direction. Since the diaphragm 2 has anisotropy that the rigidity in the circumferential direction is low, the axially symmetric vibration mode is more likely to occur.
特許文献２に記載の材料からなる振動板は、その音速が速い（剛性が高い）ため、振動板の分割共振周波数が高く、音圧周波数特性上のピーク周波数も他の樹脂材料と比較して高い。また、音圧周波数特性上のピークの数も比較的少ないという特徴がある。 Since the diaphragm made of the material described in Patent Document 2 has a high sound speed (high rigidity), the divided resonance frequency of the diaphragm is high, and the peak frequency on the sound pressure frequency characteristics is also higher than that of other resin materials. high. In addition, the number of peaks on the sound pressure frequency characteristic is relatively small.
しかし、上述の軸対称振動モードの発生は、音圧周波数特性のピーク・ディップに大きく影響を及ぼすため、音圧周波数特性上の個々のピークはいずれも急峻となり易い。ピークが急峻である場合、音のひずみが発生しやすい。 However, the occurrence of the above-described axially symmetric vibration mode greatly affects the peak dip of the sound pressure frequency characteristic, and therefore each individual peak on the sound pressure frequency characteristic tends to be steep. When the peak is steep, sound distortion tends to occur.
なお、特許文献３（特開２００５−１２３７７９号公報）には、音響機器の音圧向上を目的とした振動板の軽量化のために、振動板の厚さを薄くしたり、低密度の材料を使用したりする場合に、振動板の弾性率低下により、振動板に分割共振が発生しやすくなり、スピーカとしての音圧周波数特性を著しく悪化させてしまうという課題を解決するために、少なくとも中心部から外周方向へ放射状に３以上の奇数個設けられた厚肉部と、これらの厚肉部間をお外周から中心部に向かって徐々に厚みが薄くなるように形成した準厚肉部とでスピーカ用振動板を形成することが開示されている。ただし、振動板の弾性率低下以外の要因により、振動板に分割共振が発生しやすくなる場合についての示唆はされていない。 In Patent Document 3 (Japanese Patent Application Laid-Open No. 2005-123779), in order to reduce the weight of the diaphragm for the purpose of improving the sound pressure of an acoustic device, the thickness of the diaphragm is reduced or a low-density material is used. In order to solve the problem that split resonance is likely to occur in the diaphragm due to a decrease in the elastic modulus of the diaphragm and the sound pressure frequency characteristic as a speaker is remarkably deteriorated, at least the center is used. A thick portion provided with an odd number of 3 or more radially from the outer periphery, and a quasi-thick portion formed so that the thickness gradually decreases from the outer periphery toward the central portion between the thick portions. And forming a speaker diaphragm. However, there is no suggestion about a case where split resonance is likely to occur in the diaphragm due to factors other than a decrease in the elastic modulus of the diaphragm.
本発明は、上記の問題を解決するためになされたものであり、その目的は、出力音圧レベルを下げることなく、応答性能に優れ、かつ、音圧周波数特性上のピーク・ディップを低減できる、高音質なスピーカ用の振動板を提供することである。 The present invention has been made in order to solve the above-mentioned problems, and the object thereof is excellent in response performance without reducing the output sound pressure level, and the peak dip in the sound pressure frequency characteristic can be reduced. It is to provide a diaphragm for a speaker with high sound quality.
本発明の振動板は、スピーカ用の振動板であって、所定の中心軸に対して対称な形状を有するコーン型の振動板本体を備え、中央に設けられたボビンに巻き付けられたボイスコイルによって駆動されるコーン型の振動板である。 The diaphragm according to the present invention is a diaphragm for a speaker, and includes a cone-shaped diaphragm body having a symmetrical shape with respect to a predetermined central axis, and a voice coil wound around a bobbin provided in the center. It is a driven cone type diaphragm.
本発明の振動板は、全体が、炭素繊維強化液晶ポリマー、環状オレフィン系樹脂およびカーボンナノチューブを含む樹脂材料から構成されているため、その音速が速く、剛性が高い。そして、振動板本体の外表面の一部に突出した音質調整部材を備えるという特徴を有しているため、音圧周波数特性上のピーク・ディップに大きく寄与する軸対称振動モードの発生を抑制することができる。 Since the diaphragm of the present invention is entirely composed of a resin material containing a carbon fiber reinforced liquid crystal polymer, a cyclic olefin resin, and carbon nanotubes, its sound speed is high and rigidity is high. And since it has the characteristic of having a sound quality adjustment member protruding on a part of the outer surface of the diaphragm body, it suppresses the generation of an axially symmetric vibration mode that greatly contributes to the peak dip on the sound pressure frequency characteristics be able to.
本発明の振動板は、一般金属並みの高い音速を有する材料から構成されるため、出力音圧レベルを下げることなく、入力電気信号応答性能に優れ、かつ、音質調整部材を有するため、音圧周波数特性上のピーク・ディップに大きく寄与する軸対称振動モードの発生を抑制し、音圧周波数特性上のピーク・ディップを低減することができ、高音質を実現することができる。 Since the diaphragm of the present invention is made of a material having a high sound speed similar to that of a general metal, it has excellent input electric signal response performance without lowering the output sound pressure level and has a sound quality adjusting member, so that the sound pressure The generation of an axially symmetric vibration mode that greatly contributes to the peak dip on the frequency characteristic can be suppressed, the peak dip on the sound pressure frequency characteristic can be reduced, and high sound quality can be realized.
本発明の振動板は、スピーカ用の振動板であって、所定の中心軸に対して対称な形状を有する一般的なコーン型の振動板本体を主体としている。なお、振動板の駆動は、通常、振動板の中央部に設けられたボビンに巻き付けられたボイスコイルによって行われる。 The diaphragm of the present invention is a diaphragm for a speaker, and mainly includes a general cone-shaped diaphragm body having a symmetrical shape with respect to a predetermined central axis. The diaphragm is normally driven by a voice coil wound around a bobbin provided at the center of the diaphragm.
本発明の振動板は、少なくとも振動板本体および音質調整部材が、炭素繊維強化液晶ポリマー、環状オレフィン系樹脂およびカーボンナノチューブを含む樹脂材料から構成されている。このため、振動板の音速は速く、剛性が高い。 In the diaphragm of the present invention, at least the diaphragm main body and the sound quality adjusting member are made of a resin material containing a carbon fiber reinforced liquid crystal polymer, a cyclic olefin resin, and a carbon nanotube. For this reason, the sound speed of the diaphragm is fast and the rigidity is high.
振動板を構成する樹脂材料中の炭素繊維強化液晶ポリマーの含有量は、好ましくは５７質量％以上９０質量％以下である。また、樹脂材料中の環状オレフィン系樹脂の含有量は、好ましくは１０質量％以上３８質量％以下である。さらに、樹脂材料は、さらにカーボンナノチューブを含んでいる。樹脂材料中のカーボンナノチューブの含有量は好ましくは１０％以下である。 The content of the carbon fiber reinforced liquid crystal polymer in the resin material constituting the diaphragm is preferably 57% by mass or more and 90% by mass or less. The content of the cyclic olefin resin in the resin material is preferably 10% by mass or more and 38% by mass or less. Furthermore, the resin material further contains carbon nanotubes. The carbon nanotube content in the resin material is preferably 10% or less.
上記樹脂材料の具体例としては、５７質量％の炭素繊維強化液晶ポリマーと、３８質量％の環状オレフィン系樹脂と、５質量％のカーボンナノチューブとの混合樹脂材料が挙げられる。 Specific examples of the resin material include a mixed resin material of 57% by mass of a carbon fiber reinforced liquid crystal polymer, 38% by mass of a cyclic olefin-based resin, and 5% by mass of a carbon nanotube.
炭素繊維強化液晶ポリマーは、例えば、下記の化学式（１）、（２)および（３)で示されるポリマーから選ばれる１種類以上のポリマーから構成される。なお、化学式（１）、（２）および（３）において、ｍは１〜２０００、ｎは１〜２０００である。 The carbon fiber reinforced liquid crystal polymer is composed of, for example, one or more kinds of polymers selected from polymers represented by the following chemical formulas (1), (2), and (3). In chemical formulas (1), (2) and (3), m is 1 to 2000, and n is 1 to 2000.
環状オレフィン系樹脂は、例えば、下記の化学式（４)、（５)および（６)で示される樹脂から選ばれる１種類以上の樹脂から構成される。化学式（４）において、ｘは１〜２０００、ｙは１〜２０００である。化学式（６）において、ｎは１〜２０００、ｊは１〜２０００である。 Cyclic olefin resin is comprised from 1 or more types of resin chosen from resin shown by following Chemical formula (4), (5) and (6), for example. In the chemical formula (4), x is 1 to 2000, and y is 1 to 2000. In the chemical formula (6), n is 1 to 2000, and j is 1 to 2000.
そして、本発明の振動板は、振動板本体の外表面の一部に突出した音質調整部材とを備えるという特徴を有することにより、音圧周波数特性上のピーク・ディップに大きく寄与する軸対称振動モードの発生を抑制することができる。 The diaphragm according to the present invention includes a sound quality adjusting member that protrudes from a part of the outer surface of the diaphragm main body, and thereby has an axially symmetric vibration that greatly contributes to the peak dip in the sound pressure frequency characteristics. Mode generation can be suppressed.
少なくとも振動板本体および音質調整部材は、上記樹脂材料の射出成型によって一体成型されていることが好ましい。本発明の振動板を構成する樹脂材料は、カーボンナノチューブを含んでいるが、振動板の射出成型は、振動板中央から外周部へかけて半径方向に射出する方法が一般的であるため、得られる振動板において、射出方向は、カーボンナノチューブの繊維方向（長手方向）となるため剛性が高く、射出方向と直交する方向は、カーボンナノチューブの繊維方向と直交する方向となるため剛性が低い。このように射出成型加工によって製造された振動板は、射出方向と、射出方向に略直行する方向とで異方性を有している。 It is preferable that at least the diaphragm main body and the sound quality adjusting member are integrally formed by injection molding of the resin material. Although the resin material constituting the diaphragm of the present invention contains carbon nanotubes, the injection molding of the diaphragm is generally performed by a method of injecting in the radial direction from the center of the diaphragm to the outer peripheral portion. In the diaphragm, the emission direction is the fiber direction (longitudinal direction) of the carbon nanotubes, so that the rigidity is high, and the direction orthogonal to the injection direction is the direction orthogonal to the fiber direction of the carbon nanotubes, and thus the rigidity is low. Thus, the diaphragm manufactured by the injection molding process has anisotropy in the injection direction and the direction substantially perpendicular to the injection direction.
このように射出成型によって製造された振動板において、カーボンナノチューブの繊維方向と振動板本体の半径方向とのなす角度の平均は、通常、４５°未満であり、好ましくは３０°未満であり、より好ましくは１５°未満である。 In the diaphragm manufactured by injection molding in this way, the average angle formed by the fiber direction of the carbon nanotube and the radial direction of the diaphragm main body is usually less than 45 °, preferably less than 30 °, more Preferably it is less than 15 °.
以下、本発明のスピーカ用の振動板およびスピーカの実施形態について、図面を参照して説明するが、本発明はこれらの実施形態には限定されない。なお、以下の実施の形態において、音質調整部材は、板状または梁状であり、振動板本体の内表面に対して垂直方向に突出するように設けられる。また、図面において、同一の参照符号は、同一部分または相当部分を表すものである。また、長さ、幅、厚さ、深さなどの寸法関係は図面の明瞭化と簡略化のために適宜変更されており、実際の寸法関係を表すものではない。 Hereinafter, embodiments of a diaphragm for a speaker and a speaker of the present invention will be described with reference to the drawings, but the present invention is not limited to these embodiments. In the following embodiments, the sound quality adjusting member has a plate shape or a beam shape, and is provided so as to protrude in the vertical direction with respect to the inner surface of the diaphragm main body. In the drawings, the same reference numerals represent the same or corresponding parts. In addition, dimensional relationships such as length, width, thickness, and depth are changed as appropriate for clarity and simplification of the drawings, and do not represent actual dimensional relationships.
（実施の形態１）
図１に、実施の形態１のスピーカの全体断面図を示す。なお、ここでは、一例として、半径２００ｍのパラカーブド形状を有するスピーカ用の振動板、および、それを備えたスピーカについて説明し、その口径は１６ｃｍとする。
(Embodiment 1)
FIG. 1 shows an overall cross-sectional view of the speaker of the first embodiment. Here, as an example, a speaker diaphragm having a paracurved shape with a radius of 200 m and a speaker including the same will be described, and the aperture is 16 cm.
まず、スピーカ用の振動板について説明する。振動板本体１は、５７質量％以上９０質量％以下の炭素繊維強化液晶ポリマー、および、１０質量％以上３８質量％以下の環状オレフィン系樹脂を含み、且つ、カーボンナノチューブを含む樹脂材料の射出成型によって成型される。 First, a speaker diaphragm will be described. The diaphragm main body 1 includes 57% by mass or more and 90% by mass or less of a carbon fiber reinforced liquid crystal polymer, and 10% by mass or more and 38% by mass or less of a cyclic olefin-based resin, and an injection molding of a resin material containing carbon nanotubes. Is molded by.
振動板本体１は０．３ｍｍ程度の略均一な厚さを有し、図３の上面図においては円形であり、振動板本体１の裏面（図２における外表面１ｂ）には、射出成型の際に一体成型した音質調整部材２を有する。 The diaphragm main body 1 has a substantially uniform thickness of about 0.3 mm, is circular in the top view of FIG. 3, and is formed by injection molding on the back surface (outer surface 1b in FIG. 2) of the diaphragm main body 1. The sound quality adjusting member 2 is integrally molded.
音質調整部材２は振動板本体１の外表面１ｂに対して略直交方向に一体成型された板状の部材で、上記樹脂材料と同じ材料で構成される。音質調整部材２は、振動板本体１の内周側から外周側へかけて半径方向に直線形状であり、ここでは５本の音質調整部材２が互いに７２°の角度を持って均等に配置されている。 The sound quality adjusting member 2 is a plate-like member integrally molded in a direction substantially orthogonal to the outer surface 1b of the diaphragm main body 1, and is made of the same material as the resin material. The sound quality adjusting member 2 has a linear shape in the radial direction from the inner peripheral side to the outer peripheral side of the diaphragm main body 1. Here, the five sound quality adjusting members 2 are equally arranged with an angle of 72 ° to each other. ing.
図２を参照して、音質調整部材２の一方の端部２ｄが、振動板本体１の外周端部上に位置しており、振動板本体１の中心軸１ａの方向（中心軸１ａと平行な方向）における長さＨに対して、音質調整部材２の中心軸１ａの方向における長さＬの比率が、５０〜９０％であることが好ましい。なお、上記音質調整部材２の長さＬは、例えば、図４に示すような断面図の数値解析結果をもとに定めることができる。Ｌが短かすぎると音圧周波数特性の改善効果が得られず、逆に、Ｌが長すぎると振動板質量増加に伴う出力音圧レベルの低下につながる。図４より、Ｈに対するＬの比率が５０％以上である場合に、音圧周波数特性の有意な改善（ピークレベルの低下およびディップレベルの向上）効果が得られることが分かる。また、音質調整部材が長すぎる場合、薄いスピーカを得る際に、振動板中央寄りの音質調整部材がダンパーに接触する可能性がある。 Referring to FIG. 2, one end 2d of the sound quality adjusting member 2 is located on the outer peripheral end of the diaphragm main body 1, and is in the direction of the central axis 1a of the diaphragm main body 1 (parallel to the central axis 1a). The ratio of the length L in the direction of the central axis 1a of the sound quality adjusting member 2 to the length H in the right direction) is preferably 50 to 90%. The length L of the sound quality adjusting member 2 can be determined based on, for example, a numerical analysis result of a cross-sectional view as shown in FIG. If L is too short, the effect of improving the sound pressure frequency characteristics cannot be obtained, and conversely, if L is too long, the output sound pressure level is reduced as the diaphragm mass increases. FIG. 4 shows that when the ratio of L to H is 50% or more, a significant improvement in sound pressure frequency characteristics (decrease in peak level and improvement in dip level) can be obtained. If the sound quality adjusting member is too long, the sound quality adjusting member closer to the center of the diaphragm may come into contact with the damper when a thin speaker is obtained.
また、音質調整部材２は、図１１および図１３（ａ）に矢印で示すような軸対称振動モードの節をまたぐように配置されることが好ましい。これは、分割共振時に節となる位置では特に振動板の曲げ変形が大きくなるため、この位置に音質調整部材を設けることで、音質調整部材による曲げ変形抑制効果が最も得られるためである。音質調整部材による曲げ変形抑制効果を得ることで音圧周波数特性のピーク・ディップに影響する軸対称振動モードを抑制し、音圧周波数特性の改善効果を得ることができる。 Moreover, it is preferable that the sound quality adjusting member 2 is disposed so as to straddle the nodes of the axially symmetric vibration mode as indicated by arrows in FIGS. 11 and 13A. This is because bending deformation of the diaphragm is particularly large at a position that becomes a node at the time of split resonance, and by providing the sound quality adjusting member at this position, the bending deformation suppressing effect by the sound quality adjusting member is most obtained. By obtaining the bending deformation suppressing effect by the sound quality adjusting member, the axially symmetric vibration mode that affects the peak dip of the sound pressure frequency characteristic can be suppressed, and the sound pressure frequency characteristic improving effect can be obtained.
図２を参照して、振動板本体１の平均厚さに対して、振動板本体１の外表面１ｂを基準としたときの音質調整部材２の高さｈ（以下、単に「音質調整部材の高さ」と略すことがある）の平均値の比率が、５〜３２％であることが好ましい。振動板本体１は軸対称な形状であるので、その平均厚さは最内周付近、最外周付近、およびその中間の厚みを算術平均することで得ることができる。音質調整部材２の高さが低すぎると音圧周波数特性の改善効果が得られず、逆に、高さが高すぎると振動板質量増加に伴う出力音圧レベルの低下につながる。 Referring to FIG. 2, the height h of the sound quality adjusting member 2 with respect to the average thickness of the diaphragm main body 1 with respect to the outer surface 1b of the diaphragm main body 1 (hereinafter simply referred to as “the sound quality adjusting member”). The ratio of the average value of “which may be abbreviated as“ height ”” is preferably 5 to 32%. Since the diaphragm main body 1 has an axisymmetric shape, the average thickness can be obtained by arithmetically averaging the thicknesses near the innermost periphery, the outermost periphery, and the middle. If the height of the sound quality adjusting member 2 is too low, the effect of improving the sound pressure frequency characteristics cannot be obtained, and conversely, if the height is too high, the output sound pressure level is reduced as the diaphragm mass increases.
図５より、特に、振動板高さに対する音質調整部材の高さの比率が５％以上である場合に、音圧周波数特性の有意な改善効果が得られることが分かる。一方、同比率が増加するにしたがって、音質調整部材取付前の２０００Ｈｚ付近に見られるディップが低周波数側へ移動し、ディップのレベルが低下している。同比率が３２％である場合には、ディップレベルが音質調整部材が無い場合のディップレベルに達していることから、特に、同比率が３２％を超える場合には、ディップレベルが悪化すると考えられる。 From FIG. 5, it can be seen that a significant improvement effect of the sound pressure frequency characteristic can be obtained particularly when the ratio of the height of the sound quality adjusting member to the height of the diaphragm is 5% or more. On the other hand, as the ratio increases, the dip seen in the vicinity of 2000 Hz before the sound quality adjusting member is attached moves to the low frequency side, and the dip level is lowered. When the ratio is 32%, since the dip level has reached the dip level when there is no sound quality adjusting member, the dip level is considered to deteriorate particularly when the ratio exceeds 32%. .
図３を参照して、振動板本体１の平均厚さに対して、音質調整部材２の平均幅（幅ｗの平均値）の比率が、１０〜３００％であることが好ましい。音質調整部材２の幅が狭すぎると音圧周波数特性の改善効果が得られず、逆に、幅が厚すぎると振動板質量増加に伴う出力音圧レベルの低下につながる。 Referring to FIG. 3, the ratio of the average width (average value of width w) of sound quality adjusting member 2 to the average thickness of diaphragm main body 1 is preferably 10 to 300%. If the width of the sound quality adjusting member 2 is too narrow, an effect of improving the sound pressure frequency characteristic cannot be obtained. Conversely, if the width is too thick, the output sound pressure level is reduced due to an increase in diaphragm mass.
図６より、特に、振動板本体の平均厚さに対する音質調整部材の平均幅の比率が１０％以上である場合に、音圧周波数特性の有意な改善効果が得られることが分かる。一方、同比率が３００％である場合には、ディップレベルが音質調整部材が無い場合のディップレベルとほぼ同等となっていることから、特に、同比率が３００％を超える場合には、ディップレベルが悪化すると考えられる。また、同比率が３００％である場合には、全体音圧の低下も見られ、その低下量の平均が１ｄＢ弱となっている。このため、同比率が３００％を超える場合には、出力音圧レベルが有意に低下してしまうと考えられる。 From FIG. 6, it can be seen that a significant improvement effect of the sound pressure frequency characteristic can be obtained particularly when the ratio of the average width of the sound quality adjusting member to the average thickness of the diaphragm main body is 10% or more. On the other hand, when the ratio is 300%, the dip level is almost the same as the dip level when there is no sound quality adjusting member. Therefore, when the ratio exceeds 300%, the dip level is particularly high. Is thought to worsen. Further, when the ratio is 300%, a decrease in the overall sound pressure is also observed, and the average amount of the decrease is less than 1 dB. For this reason, when the ratio exceeds 300%, the output sound pressure level is considered to decrease significantly.
なお、上記の音質調整部材の寸法の上限値は、振動板の質量に対する音質調整部材の質量比で決まる出力音圧のレベル低下量に依存する。図７は、振動板の質量に対する音質調整部材の質量の比率と、出力音圧のレベル低下量との関係を示すグラフである。つまり、音質調整部材の長さ、高さおよび幅の各寸法は上記の範囲内で、且つ、出力音圧のレベル低下量が１ｄＢ下となるように、振動板の質量に対する音質調整部材の質量の比率が７．２％以下とすることが好ましい。 The upper limit value of the dimension of the sound quality adjusting member depends on the level reduction amount of the output sound pressure determined by the mass ratio of the sound quality adjusting member to the mass of the diaphragm. FIG. 7 is a graph showing the relationship between the ratio of the mass of the sound quality adjusting member to the mass of the diaphragm and the level reduction amount of the output sound pressure. That is, the length, height, and width of the sound quality adjustment member are within the above ranges, and the mass of the sound quality adjustment member with respect to the mass of the diaphragm is such that the amount of decrease in the level of the output sound pressure is 1 dB. The ratio is preferably 7.2% or less.
図２に示す音質調整部材２の側面の両端（端部２ｃ，２ｄ）には、射出成型時における樹脂材料の流動性を考慮した湾曲部を設け、また、図８に示す音質調整部材２の断面における振動板本体１との接合部分２ｅにも、同様に樹脂材料の流動性を考慮した湾曲部を設けている。これにより、射出成型の際の樹脂材料の流動性を高め、音質調整部材２となる箇所への充填不良を防ぐことができる。湾曲部の曲率（Ｒ）は、樹脂材料の流動性を高め、充填不良を防ぐために、０．５〜１．０であることが好ましい。曲率が大きすぎると、振動板質量増加に伴う出力音圧レベルの低下につながる。なお、このような湾曲部で射出成型時の樹脂材料の流れを変化させ、部分的に異方性を持たせることも可能である。 2 are provided at both ends (ends 2c, 2d) of the side surface of the sound quality adjusting member 2 shown in FIG. 2 in consideration of the fluidity of the resin material at the time of injection molding, and the sound quality adjusting member 2 shown in FIG. Similarly, a curved portion in consideration of the fluidity of the resin material is provided in the joint portion 2e with the diaphragm main body 1 in the cross section. Thereby, the fluidity | liquidity of the resin material in the case of injection molding can be improved, and the filling defect to the location used as the sound quality adjustment member 2 can be prevented. The curvature (R) of the curved portion is preferably 0.5 to 1.0 in order to increase the fluidity of the resin material and prevent poor filling. If the curvature is too large, the output sound pressure level will decrease as the diaphragm mass increases. In addition, it is also possible to change the flow of the resin material at the time of injection molding by such a curved part, and to give anisotropy partially.
次に、上記の音質調整部材２を一体成型した振動板本体１を有するコーン型スピーカの構成について説明する。 Next, the structure of the cone type speaker having the diaphragm main body 1 integrally molded with the sound quality adjusting member 2 will be described.
図１に示すとおり、振動板の外周部にはロール形状のエッジ部４を有する。エッジ部４の内周側は振動板本体１の上面に貼り付けられており、その外周側はガスケット５を用いてフレーム６に固定されている。振動板本体１の中央開口部には円筒形状のボビン７が内接されており、その周囲にはボイスコイル８が巻き付けられている。 As shown in FIG. 1, the outer peripheral portion of the diaphragm has a roll-shaped edge portion 4. The inner peripheral side of the edge portion 4 is affixed to the upper surface of the diaphragm main body 1, and the outer peripheral side is fixed to the frame 6 using a gasket 5. A cylindrical bobbin 7 is inscribed in the central opening of the diaphragm body 1, and a voice coil 8 is wound around it.
ボビン７の振動側端部を覆うようにダストキャップ３が振動板本体１に取り付けられ、ボビン７の他端部にはボビン７の位置を確定するためのポールピース９が取り付けられている。ポールピース９の上にはマグネット１０が固定され、マグネット１０の上にはヨーク１１が固定されている。ヨーク１１の内周は前記ボイスコイル８と磁気ギャップを有する内径が定められている。 A dust cap 3 is attached to the diaphragm main body 1 so as to cover the vibration side end of the bobbin 7, and a pole piece 9 for fixing the position of the bobbin 7 is attached to the other end of the bobbin 7. A magnet 10 is fixed on the pole piece 9, and a yoke 11 is fixed on the magnet 10. The inner circumference of the yoke 11 has an inner diameter having a magnetic gap with the voice coil 8.
上述のエッジ部４が固定されたフレーム６の下端は、ヨーク１１に固定されており、スピーカ全体の強度部材として用いられる。ボビン７の略中間部にはコルゲーション形状のダンパー１２が取り付けられ、外周部は前記フレーム６と接合されている。 The lower end of the frame 6 to which the edge portion 4 is fixed is fixed to the yoke 11 and used as a strength member for the entire speaker. A corrugation-shaped damper 12 is attached to a substantially middle portion of the bobbin 7, and an outer peripheral portion is joined to the frame 6.
本実施の形態では、上記の樹脂材料を使用することで金属並みの音速を有する振動板を得ることが出来るため、信号入力に対して応答性能のよいスピーカ用の振動板およびスピーカを得ることが出来る。また、剛性が高いため、振動板の分割共振周波数が高く、スピーカ使用周波数範囲内に生じる音圧のピーク・ディップの数が比較的少ないスピーカ用の振動板およびスピーカを得ることが出来る。 In the present embodiment, a diaphragm having a sound speed similar to that of a metal can be obtained by using the resin material described above. Therefore, a diaphragm for a speaker and a speaker having good response performance with respect to signal input can be obtained. I can do it. Further, since the rigidity is high, it is possible to obtain a diaphragm and a speaker for a speaker that have a high divided resonance frequency of the diaphragm and a relatively small number of peak dip of sound pressure generated in the speaker operating frequency range.
さらに、音質調整部材２を有することで、図９に示すとおり、前記材料の射出成型に伴って生じる振動板周方向の材料および形状の均一性を変化させることができ、音圧周波数特性上のピーク・ディップに大きく影響を及ぼす軸対称振動モードを抑制することが出来る。これによって、図１２に示した音質調整部材がない振動板（後述する比較形態の振動板）における音圧周波数特性および２次高調波歪みを、図１０のように改善することができる。具体的には、音圧周波数特性上のピーク・ディップが大きく改善される。このように、２次の高調波ひずみを大幅に低減することが可能となり、劇的に音質が改善されたスピーカ用の振動板およびスピーカを得ることが可能となる。 Furthermore, by having the sound quality adjusting member 2, as shown in FIG. 9, it is possible to change the uniformity of the material and the shape in the circumferential direction of the diaphragm caused by the injection molding of the material. Axisymmetric vibration modes that greatly affect peak dip can be suppressed. As a result, the sound pressure frequency characteristics and second harmonic distortion in the diaphragm without the sound quality adjusting member shown in FIG. 12 (comparative diaphragm described later) can be improved as shown in FIG. Specifically, the peak dip on the sound pressure frequency characteristic is greatly improved. As described above, it is possible to significantly reduce the second-order harmonic distortion, and it is possible to obtain a speaker diaphragm and a speaker with dramatically improved sound quality.
（比較形態）
比較形態として、実施の形態１と同様の材料を用いた射出成型により製造される、音質調整部材を備えていない従来のコーン型の振動板について説明する。
(Comparison form)
As a comparative example, a conventional cone-type diaphragm that is manufactured by injection molding using the same material as in the first embodiment and does not include a sound quality adjusting member will be described.
図１１は、比較形態の振動板について、その中心軸を基準とした軸対称振動モードと軸対称振動モードの節の一例を示す模式図である。射出成型による振動板の製造においては、均質な材料分布および均一な振動板形状が得られるため、比較形態の振動板の分割共振状態において、振動板の中心軸を基準とした軸対称の振動モードが生じやすい（図１１参照）。さらに、比較形態の振動板は、周方向の剛性が低いという異方性を有しているため、軸対称振動モードはより一層生じやすくなる。このような軸対称振動モードが生じた場合、振動板の分割共振が発生して、音圧周波数特性上にピーク・ディップが発生し、音質を著しく悪化させてしまう。 FIG. 11 is a schematic diagram illustrating an example of a node of an axially symmetric vibration mode and an axially symmetric vibration mode with respect to the central axis of the diaphragm according to the comparative embodiment. In the production of diaphragms by injection molding, a homogeneous material distribution and uniform diaphragm shape can be obtained, so in the split resonance state of the diaphragm of the comparative form, an axially symmetric vibration mode with respect to the central axis of the diaphragm Is likely to occur (see FIG. 11). Furthermore, since the diaphragm of the comparative form has anisotropy that the rigidity in the circumferential direction is low, an axially symmetric vibration mode is more likely to occur. When such an axially symmetric vibration mode occurs, a divided resonance of the diaphragm occurs, a peak dip occurs on the sound pressure frequency characteristics, and the sound quality is significantly deteriorated.
図１２は、比較形態の振動板を備えたスピーカの一例について、音圧周波数特性および２次高調波歪みの測定結果を示す図である。図１２に示されるように、比較形態の振動板は、実施の形態１と同様に、構成材料の音速が速い（剛性が高い）ため、振動板の分割共振周波数、および、音圧周波数特性上のピーク周波数が他の樹脂材料と比較して高く、また、ピークの数も比較的少ないという特徴を有している。 FIG. 12 is a diagram illustrating measurement results of sound pressure frequency characteristics and second-order harmonic distortion for an example of a speaker including a comparative diaphragm. As shown in FIG. 12, the diaphragm according to the comparative example has a high sound speed (high rigidity) of the constituent material, as in the first embodiment. Therefore, the diaphragm has a resonance frequency characteristic and a sound pressure frequency characteristic. The peak frequency is higher than other resin materials, and the number of peaks is relatively small.
しかし、図１２に示される個々のピークは、いずれも、実施の形態１における図１０に示されるピークと比べて急峻である。これは、上記の軸対称振動モードの影響であると考えられる。 However, each of the individual peaks shown in FIG. 12 is steep compared to the peak shown in FIG. 10 in the first embodiment. This is considered to be an influence of the above-described axially symmetric vibration mode.
（実施の形態２）
実施の形態２の振動板は、実施の形態１に対し、音質調整部材の形状が異なる他は、共通するスピーカ用の振動板およびスピーカである。
(Embodiment 2)
The diaphragm according to the second embodiment is a common diaphragm for a speaker and a speaker except that the shape of the sound quality adjusting member is different from that of the first embodiment.
実施の形態１では、音質調整部材の高さが一定である。これに対し、実施の形態２では、図１３（ｂ）中の矢印で示す振動板の軸対称振動モードの節位置で、図１４に示すように音質調整部材２の高さが特に高くなっている。つまり、振動板の軸対称振動モードの節位置以外の音質調整部材２の高さを相対的に低くすることが出来る。このため、軸対称のモードの節位置で特に音質調整部材が作用し、軸対称のモードを効率よく抑制することが出来る。 In the first embodiment, the height of the sound quality adjusting member is constant. On the other hand, in the second embodiment, the height of the sound quality adjusting member 2 is particularly high as shown in FIG. 14 at the node position of the axially symmetric vibration mode of the diaphragm indicated by the arrow in FIG. Yes. That is, the height of the sound quality adjusting member 2 other than the node position in the axially symmetric vibration mode of the diaphragm can be relatively lowered. For this reason, the sound quality adjusting member acts particularly at the node position of the axially symmetric mode, and the axially symmetric mode can be efficiently suppressed.
本発明の振動板を構成する樹脂材料は、音速が速いため、振動板が分割振動を始める周波数が高い。このため、スピーカ使用周波数帯域内に現れるモード数が少なく、軸対称のモードの節となる位置を狙って音質調整部材の形状を決定することが可能である。 Since the resin material constituting the diaphragm of the present invention has a high sound speed, the frequency at which the diaphragm starts split vibration is high. For this reason, the number of modes appearing in the speaker use frequency band is small, and the shape of the sound quality adjusting member can be determined aiming at a position that becomes a node of an axially symmetric mode.
また、軸対称振動モードの節位置で、高さ以外に、音質調整部材の幅を広くしてもよい。なお、本実施の形態においても、図７のように振動板質量に対する音質調整部材の質量比による出力音圧レベルの低下を考慮した音質調整部材形状とする。 In addition to the height, the width of the sound quality adjusting member may be widened at the node position in the axially symmetric vibration mode. In the present embodiment as well, the shape of the sound quality adjusting member is set in consideration of a decrease in the output sound pressure level due to the mass ratio of the sound quality adjusting member to the diaphragm mass as shown in FIG.
このような構成によれば、振動板の軸対称振動モードの節以外の位置の音質調整部材を削減したまま、音圧周波数特性のピーク・ディップに大きく影響を及ぼす振動板の軸対称の振動モードを効率よく抑制できる。つまり、音質調整部材の軽量化およびコスト削減を実現したまま、音圧周波数特性のピーク・ディップを改善することが可能となる。 According to such a configuration, the axially symmetric vibration mode of the diaphragm that greatly affects the peak dip of the sound pressure frequency characteristic while reducing the sound quality adjusting members at positions other than the nodes of the axially symmetric vibration mode of the diaphragm. Can be efficiently suppressed. That is, it is possible to improve the peak dip of the sound pressure frequency characteristic while realizing the weight reduction and cost reduction of the sound quality adjusting member.
（実施の形態３）
実施の形態３の振動板は、実施の形態１に対して音質調整部材の形状が異なる他は、実施の形態１と同様のスピーカ用の振動板およびスピーカである。
(Embodiment 3)
The diaphragm of the third embodiment is the same diaphragm and speaker for the speaker as in the first embodiment except that the shape of the sound quality adjusting member is different from that in the first embodiment.
実施の形態１では、音質調整部材の高さおよび幅が一定である。これに対して、実施の形態３では、図１５および図１６に示すように、音質調整部材２の高さは、中心軸側２ａから外周端部２ｂに向かうにしたがって高くなり、反対に、音質調整部材２の幅は、前記振動板の中心軸側２ａから外周端部２ｂへ向かうにしたがって狭くなる。このように、振動板の半径方向において、音質調整部材の高さと共に幅も変化させることで、音質調整部材の断面積（振動板の半径方向に垂直な断面での断面積）の変化を小さくすることができる。 In the first embodiment, the height and width of the sound quality adjusting member are constant. On the other hand, in the third embodiment, as shown in FIGS. 15 and 16, the height of the sound quality adjusting member 2 increases from the central axis side 2a toward the outer peripheral end 2b. The width of the adjusting member 2 becomes narrower from the central axis side 2a of the diaphragm toward the outer peripheral end 2b. Thus, by changing the height and width of the sound quality adjusting member in the radial direction of the diaphragm, the change in the cross-sectional area of the sound quality adjusting member (the cross-sectional area in the cross section perpendicular to the radial direction of the diaphragm) is reduced. can do.
一方、図１７や図１８のように音質調整部材２の断面積（振動板の半径方向に垂直な断面での断面積）を一定とする形状でもよい。図１７は高さの変化を直線形状にし、断面積が一定となるように幅を曲線形状とし、反対に、図１８は幅の変化を直線形状にし、断面積が一定となるように高さを曲線形状としている。なお、本実施の形態においても、図７のように振動板質量に対する音質調整部材の質量比による出力音圧レベルの低下を考慮した音質調整部材形状とすることが好ましい。 On the other hand, as shown in FIGS. 17 and 18, the sound quality adjusting member 2 may have a constant cross-sectional area (cross-sectional area in a cross section perpendicular to the radial direction of the diaphragm). FIG. 17 shows a straight line shape with a change in height and a curved shape so that the cross-sectional area is constant. On the other hand, FIG. 18 shows a straight line shape with a change in width and a constant cross-sectional area. Is a curved shape. Also in the present embodiment, it is preferable that the sound quality adjusting member has a shape that takes into account the decrease in the output sound pressure level due to the mass ratio of the sound quality adjusting member to the diaphragm mass as shown in FIG.
このような構成によれば、振動板の軸対称振動モードの最低次モードにおいて振動の節となる振動板外周部で、音質調整部材の高さを高くすることが出来るため、特に軸対称振動モードの最低次周波数における、音圧周波数特性のピーク・ディップを改善することが可能となる。また、音質調整部材の振動板中央側の幅が広く、振動板外周側が狭いため、振動板中央から外周部へ向かって射出成型する際に、音質調整部材の幅が広い側から狭いほうへ樹脂を流動させるため、樹脂材料の流動不良が生じ難くなり、確実な音質調整部材の成型が可能となる。 According to such a configuration, the height of the sound quality adjusting member can be increased at the outer peripheral portion of the diaphragm that becomes a node of vibration in the lowest order mode of the axially symmetric vibration mode of the diaphragm. It is possible to improve the peak dip of the sound pressure frequency characteristic at the lowest order frequency. In addition, since the width of the sound quality adjusting member is wide on the center side of the diaphragm and the outer peripheral side of the diaphragm is narrow, when injection molding is performed from the center of the diaphragm toward the outer periphery, the resin from the wide side of the sound quality adjusting member to the narrow side Therefore, it is difficult for the resin material to flow poorly, and the sound quality adjusting member can be reliably molded.
なお、上記の実施の形態における振動板の形状は、パラカーブド形状以外のストレート形状、パラボリック形状などであってもよい。振動板の曲率および口径についても、上記の数値に限るものではなく、例えば１０ｃｍ、１５ｃｍ口径のスピーカにおいても、上記と同じ音質調整部材によって音圧周波数特性および２次高調波特性の改善効果が得られる。 In addition, the shape of the diaphragm in the above embodiment may be a straight shape other than the paracurved shape, a parabolic shape, or the like. The curvature and aperture of the diaphragm are not limited to the above values. For example, even in a 10 cm or 15 cm aperture speaker, the same sound quality adjusting member as described above can improve the sound pressure frequency characteristics and the second harmonic characteristics. can get.
また、音質調整部材２の寸法・本数についても上記寸法の限りではない。ただし、図２０の結果より、音質調整部材の本数は上記のごとく特に５本の場合において、最も音圧周波数特性の改善効果が得られる。また、射出成型による樹脂流動が成立する限り、音質調整部材を曲線状にすることも可能であり、図１９のように各音質調整部材の配置間隔も均等である必要はない。 Further, the dimensions and number of the sound quality adjusting members 2 are not limited to the above dimensions. However, from the result of FIG. 20, when the number of the sound quality adjusting members is particularly five as described above, the effect of improving the sound pressure frequency characteristic is most obtained. Further, as long as the resin flow by injection molding is established, the sound quality adjusting member can be curved, and the arrangement intervals of the sound quality adjusting members do not need to be uniform as shown in FIG.
今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.
１ 振動板本体、１ａ 中心軸、１ｂ 外表面、２ 音質調整部材、２ａ 中心軸側、２ｂ 外周端部、２ｃ，２ｄ 端部、２ｅ 接合部分、３ ダストキャップ、４ エッジ部、７ ボビン、８ ボイスコイル、９ ポールピース、１０ マグネット、１１ ヨーク、１２ ダンパー。 DESCRIPTION OF SYMBOLS 1 Diaphragm main body, 1a center axis | shaft, 1b outer surface, 2 sound quality adjustment member, 2a center axis side, 2b outer periphery edge part, 2c, 2d edge part, 2e joining part, 3 dust cap, 4 edge part, 7 bobbin, 8 Voice coil, 9 pole piece, 10 magnet, 11 yoke, 12 damper.
Claims (16)
所定の中心軸に対して対称な形状を有するコーン型の振動板本体と、前記振動板本体の外表面の一部に突出した音質調整部材とを備え、
前記音質調整部材は、板状または梁状であり、前記振動板本体の内表面に対して垂直方向に突出するように設けられており、
前記振動板本体の外表面を基準としたときの前記音質調整部材の高さが、前記振動板の軸対称分割振動モードの節において、他の部位よりも高いことを特徴とする、振動板。 A cone-shaped diaphragm for a speaker,
A cone-shaped diaphragm main body having a symmetrical shape with respect to a predetermined central axis, and a sound quality adjusting member protruding from a part of the outer surface of the diaphragm main body,
The sound quality adjusting member has a plate shape or a beam shape, and is provided so as to protrude in a direction perpendicular to the inner surface of the diaphragm main body,
The diaphragm according to claim 1, wherein a height of the sound quality adjusting member with respect to an outer surface of the diaphragm main body is higher than other portions in a node of the axially symmetric divided vibration mode of the diaphragm.
前記振動板本体の前記中心軸の方向における長さに対して、前記音質調整部材の前記中心軸の方向における長さの比率が、５０〜９０％である、請求項１に記載の振動板。 One end of the sound quality adjusting member is located on the outer peripheral end of the diaphragm main body,
The diaphragm according to claim 1, wherein a ratio of a length of the sound quality adjusting member in the direction of the central axis to a length of the diaphragm main body in the direction of the central axis is 50 to 90%.
前記音質調整部材の幅が、前記振動板の中心軸側から外周端部へ向かうにしたがって狭くなる、請求項１に記載の振動板。 The height of the sound quality adjusting member when the outer surface of the diaphragm main body is used as a reference increases from the central axis side of the diaphragm toward the outer peripheral end, and
The diaphragm according to claim 1, wherein a width of the sound quality adjusting member becomes narrower from a center axis side of the diaphragm toward an outer peripheral end.
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| JP6699033B2 (en) * | 2015-09-29 | 2020-05-27 | 三菱電機株式会社 | Speaker diaphragm and speaker |
| US10547942B2 (en) | 2015-12-28 | 2020-01-28 | Samsung Electronics Co., Ltd. | Control of electrodynamic speaker driver using a low-order non-linear model |
| US10462565B2 (en) | 2017-01-04 | 2019-10-29 | Samsung Electronics Co., Ltd. | Displacement limiter for loudspeaker mechanical protection |
| US10506347B2 (en) | 2018-01-17 | 2019-12-10 | Samsung Electronics Co., Ltd. | Nonlinear control of vented box or passive radiator loudspeaker systems |
| US10701485B2 (en) | 2018-03-08 | 2020-06-30 | Samsung Electronics Co., Ltd. | Energy limiter for loudspeaker protection |
| WO2019178797A1 (en) * | 2018-03-22 | 2019-09-26 | Green Energy Engineering Consultancy Limited | Device with external diaphragm for acoustic cleaning and air purification applications |
| US10542361B1 (en) | 2018-08-07 | 2020-01-21 | Samsung Electronics Co., Ltd. | Nonlinear control of loudspeaker systems with current source amplifier |
| US11012773B2 (en) | 2018-09-04 | 2021-05-18 | Samsung Electronics Co., Ltd. | Waveguide for smooth off-axis frequency response |
| US10797666B2 (en) | 2018-09-06 | 2020-10-06 | Samsung Electronics Co., Ltd. | Port velocity limiter for vented box loudspeakers |
| US11356773B2 (en) | 2020-10-30 | 2022-06-07 | Samsung Electronics, Co., Ltd. | Nonlinear control of a loudspeaker with a neural network |
| CN112511956B (en) * | 2020-11-02 | 2023-04-28 | 歌尔股份有限公司 | Vibrating plate for sound generating device and sound generating device |
| CN114827871B (en) * | 2021-01-29 | 2023-07-14 | 歌尔股份有限公司 | Vibrating diaphragm and sound producing device |
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| JPH0346296U (en) * | 1989-09-12 | 1991-04-30 | ||
| JP2012138887A (en) * | 2010-12-08 | 2012-07-19 | Panasonic Corp | Diaphragm, and speaker device equipped with the same |
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