JP3099805U - Panel speaker with composite laminate - Google Patents

Abstract

A panel-type speaker made of a composite laminate characterized in that sound pressure sensitivities relatively uniformly distributed in a relatively wide frequency range are generated.
A loudspeaker composite laminate and a high-efficiency loudspeaker are divided into a high-efficiency loudspeaker area in a high-efficiency loudspeaker area. , A panel-type speaker comprising a plurality of vibrators 50 for performing flexible vibration.
[Selection diagram] Fig. 1

Description

(4) The present invention relates to a panel-type speaker capable of obtaining a high-efficiency loudspeaker function by generating effective vibration deformation in a specific frequency range.

Issues to be solved by the background art and the invention

Traditional loudspeakers mainly use a conical film as the loudspeaker utterance mechanism. The conical film has a relatively small end connected to an electromagnetic coil type vibrator, and the conical film vibrates back and forth by driving the vibrator to push the air to achieve the purpose of sound enhancement. Generally, this type of speaker requires an audio box to prevent sound waves in front of the speaker from being interfered by reverse sound waves from behind, but the sound box not only makes the speaker heavy, but also causes blind spots in sound transmission. .

Because traditional loudspeakers have the above-mentioned drawbacks, the development of panel-type loudspeakers has been deeply sought, and in recent years, many ideas in this field have appeared. For example, Waters uses a concept of a synchronization frequency, that is, a light-weight, highly-energized, long-range loudspeaker using the same frequency of sound in the air and the speed of propagation of a flexible wave on a flat plate due to the synchronization frequency. The board has been designed so that flexible waves can be transmitted and high directional speech can be produced within a specific frequency range. Also, Heron designed the panel-type speaker using the method of the natural vibration mode of the tremor loudspeaker, but in this design, a beehive sandwich plate was used as the loudspeaker, and the plate member was violently shaken at one corner of the sandwich plate. A vibrator for generating flexible vibration is provided, thereby outputting a sound whose frequency is higher than the basic natural frequency and the periodic frequency of the loudspeaker, thereby improving the loudspeaker efficiency. However, since the flat plate provided by these methods has extremely high rigidity, the loudspeaker plate must be driven by using a large and heavy seismic shaker. Its efficiency is lower than traditional speakers. Also, the frequency range to which the utterance of the loudspeaker belongs is narrow for general use, and can only be used for public speech. Azima et al. Also designed a panel-type speaker using the method of the natural vibration mode of the seismic loudspeaker, but the seismic device used in this design was placed at a specific position on the panel, and as far as possible in front of the plate. Most modes of the board are violently shaken so as not to overlap the nodal line of the 20-25 natural modes, and the air is driven to achieve the purpose of loudspeaking. This type of vibrating loudspeaker can obtain a relatively wide voice frequency, but its facsimile effect is not ideal. Because on a flat plate, there may be thousands of natural frequencies and modes between 50Hz and 20kHz, and determining the position of a seismic device based on only the previous 20 Since the sound pressure suddenly increases due to excessive seismic force in a certain natural mode within the range, or a sudden drop in sound pressure due to the overlap of the nodal line and the seismic position of another natural mode. The panel-type speaker designed based on it generates a frequency spectrum of high and low undulating sound pressure sensitivity, which affects its facsimile effect. On the other hand, the design causes the seismic position to be farther away from the nodal line of the previous 20 or so modes, and all of these modes are exploded, but in the antisymmetric mode, the forward and backward motions The regions have opposite phases, and the sound pressures generated by these regions interfere with each other and severely affect the magnitude of the sound pressure sensitivity. In short, there are many drawbacks to be improved in the currently widely used panel type speakers.

In order to overcome the difficulties and limitations faced by the above panel-type speakers, the present inventor has developed a composite laminate characterized in that relatively uniformly distributed sound pressure sensitivity is generated within a relatively wide frequency range. We designed a panel-type speaker.

The panel-type speaker of the present invention has a composite laminate for loudspeakers and two high-performance and low-efficiency loudspeaker regions on the panel, and the composite loudspeaker is driven in the high-performance loudspeaker region. This is provided with a plurality of vibrators for performing flexible vibration. A plurality of biasing strips having different stiffness and adjusting the vibration mode and the distribution of the sound pressure sensitivity frequency spectrum of the loudspeaker composite laminate are separately formed around the composite laminate. A further effect of the biasing strip is to reduce the generation of noise by suppressing the high frequency standing waves that are stagnating around the perimeter of the laminate. The periphery of the loudspeaker composite laminate is separately connected to a soft suspension system for suspending the loudspeaker board on a frame or fixed object. The loudspeaking efficiency and sound quality of this panel type speaker are determined by, for example, the lamination method of the composite laminate, the ratio of the composite module to the weight density, the stiffness of the biasing strip, and the position of the vibrator in the high-performance loudspeaker area. Related to the parameter. Therefore, when designing a panel-type speaker of a composite laminate, it is necessary to select appropriate parameters that generate an appropriate magnitude and distribution of sound pressure sensitivity within the audio frequency range required by the speaker.

1. The design method and the use of the program flat plate as the source is to generate air by contacting the plate surface by generating a flexible vibration, and to determine the magnitude of the generated sound pressure using a vocal method and related equations. That's why. For an infinitely extending flat plate or a flat plate whose size is finite and whose periphery is sealed, the sound pressure generated at any one point in the space of the flat plate vibration is Rayleigh's first integral. And the instantaneous sound pressure at the point is expressed by the following equation (1).

（１）
　式中Ｐ（ｒ，ｔ）は板面からｒ離れた個所の瞬時音圧、ｒは計測点と板面上の参考座標原点との距離、Ｒは計測点と板面上の一振動点との間の距離、ｒｓは振動点と座標原点との間の距離、ρｏは空気密度、ｔは時間、Ｓは板の面積、ωは平板の振動周波数、Ｄ（ｒｓ）は振動点の側方向シフト応答、ｉ＝√−１である。上式におけるD(rs)は有限素子方法により平板の動態応答を分析して求められる。なお、モード分析から板の側方向シフト応答は各モードの側方向シフト応答の総和であることが確認され、下記式（２）で表される。

(1)
In the formula, P (r, t) is the instantaneous sound pressure at a point r away from the plate surface, r is the distance between the measurement point and the reference coordinate origin on the plate surface, and R is the measurement point and one vibration point on the plate surface. , Rs is the distance between the vibration point and the coordinate origin, ρo is the air density, t is time, S is the area of the plate, ω is the vibration frequency of the plate, and D (rs) is the side direction of the vibration point. Shift response, i = √−1. D (rs) in the above equation is obtained by analyzing the dynamic response of the flat plate by the finite element method. It is confirmed from the mode analysis that the lateral shift response of the plate is the sum of the lateral shift responses of the respective modes, and is expressed by the following equation (2).

（２）
　式中、ｎは考慮される自然モードの個数、Ａｉ及びφｉはそれぞれ第一個の自然モードの振幅及び振動型である。式（１）及び（２）から、固定計測点は瞬時音圧の大きさと板の振動周波数と板の自然モードパラメータとに関連していることが分かる。また、板の面積が限られていれば、式（１）から瞬時音圧も板と関連して、面積の大きい方の板が比較的大きな音圧を生ずることが分かる。ここに定義された音圧の感度は次の式で表される。

(2)
Where n is the number of natural modes considered, Ai and φi are the amplitude and vibration type of the first natural mode, respectively. From equations (1) and (2), it can be seen that the fixed measurement point is related to the magnitude of the instantaneous sound pressure, the vibration frequency of the plate and the natural mode parameters of the plate. Also, if the area of the plate is limited, Equation (1) shows that the instantaneous sound pressure also relates to the plate, and the plate with the larger area generates a relatively large sound pressure. The sensitivity of the sound pressure defined here is expressed by the following equation.

（３）
　式中、Ｌｐは音圧感度、Ｐｒｍｓは音圧、平方の根平均自乗値、Ｐｒｅｆは参考圧力定数である。同様に式（１）及び（３）から、音圧感度は平板の振動周波数、自然モードパラメータ及び板の面積に関連することが分かる。異なる振動周波数で分析された音圧感度は拡声板の音圧感度周波数スペクトルを得ることが可能であり、そして比較的広い範囲内で比較的均一な音圧感度分布を得ることは高描写力を有するパネル形スピーカの設計に不可欠な条件である。また、拡声板の面積が変化しない場合、その音圧感度周波数スペクトルの分布を影響するものは板の振動周波数及び自然モードパラメータである。なお、板の振動周波数とその自然周波数が同一である場合は共振現象を起し、該周波数の自然モードの振幅が大きくなるので、この周波数の音圧感度が明白に向上される。従って、板の設計は発生した音圧感度が特定の周波数範囲内であまり大きな変化がないように、その自然振動周波数の分布を考慮しなければならない。 拡声板に用いられる複合物の性質及びその積層方式はいずれも直接平板の自然周波数、振幅、振動型等のモードのパラメータに影響を及ぼすので拡声板の音圧感度周波数スペクトル分布に影響する。一般に、材質が軽量で付勢力の高い平板は比較的好適な拡声効果を生ずる。激震器の板上の高効能拡声領域に配置された位置は直接各自然モードの振幅に影響を及ぼし、そのために拡声板で発生した音圧感度スペクトルの分布状況に影響を及ぼすことから、激震器の配置地点は音圧感度を増加する必要があるばかりでなく、音圧感度を特定の周波数範囲にて比較的均一に分布させるようにしなければならない。他方、反対のシフト位相角を有する自然モード振動型については、前後方への運動により生じる音圧は位相が反対であるために相互干渉してしまい、厳重に振動周波数の音圧感度を低下させる。このような音圧の干渉現象は通常中、低周波数範囲内において比較的明白に現れる。拡声板の周囲に剛度のそれぞれ異なる付勢ストリップを付加形成すると、好適な付熱ストリップの剛度分布を選択する事により拡声板の自然モード振動型を調整することができ、これにより異なる位相角の音圧間の干渉を減少させ、その音圧感度を増加させる。

(3)
In the equation, Lp is sound pressure sensitivity, Prms is sound pressure, root mean square value of square, and Pref is a reference pressure constant. Similarly, from equations (1) and (3), it can be seen that the sound pressure sensitivity is related to the vibration frequency of the flat plate, the natural mode parameter, and the area of the plate. The sound pressure sensitivity analyzed at different vibration frequencies makes it possible to obtain the sound pressure sensitivity frequency spectrum of the loudspeaker, and to obtain a relatively uniform sound pressure sensitivity distribution within a relatively wide range requires high definition. This is an indispensable condition for the design of a panel-type speaker. When the area of the loudspeaker does not change, the distribution of the sound pressure sensitivity frequency spectrum is affected by the vibration frequency and the natural mode parameter of the loudspeaker. When the vibration frequency of the plate is the same as its natural frequency, a resonance phenomenon occurs, and the amplitude of the natural mode of the frequency increases, so that the sound pressure sensitivity at this frequency is clearly improved. Therefore, the design of the board must take into account its natural vibration frequency distribution so that the generated sound pressure sensitivity does not change significantly within a specific frequency range. The properties of the composite used for the loudspeaker and the lamination method directly affect the parameters of the mode such as the natural frequency, amplitude, and vibration type of the flat plate, and thus affect the sound pressure sensitivity frequency spectrum distribution of the loudspeaker. In general, a flat plate made of a lightweight material and having a high urging force produces a relatively favorable sound enhancement effect. Positions located in the high-efficiency loudspeaker area on the plate of the tremor directly affect the amplitude of each natural mode, which in turn affects the distribution of the sound pressure sensitivity spectrum generated by the loudspeaker. In addition to the need to increase the sound pressure sensitivity, the location must be such that the sound pressure sensitivity is relatively uniformly distributed in a specific frequency range. On the other hand, in the case of the natural mode vibration type having the opposite shift phase angle, the sound pressures generated by the forward and backward movements interfere with each other because the phases are opposite, and severely reduce the sound pressure sensitivity of the vibration frequency. . Such sound pressure interference phenomena usually appear relatively clearly in the low frequency range. By additionally forming energizing strips having different stiffnesses around the loudspeaker plate, it is possible to adjust the natural mode vibration type of the loudspeaker plate by selecting a suitable stiffness distribution of the heating strip, thereby providing different phase angles. It reduces interference between sound pressures and increases their sound pressure sensitivity.

設計 Thus, design parameters that affect the distribution of the sound pressure sensitivity frequency spectrum of the loudspeaker are the material properties of the loudspeaker composite laminate, the lamination method of the laminate, the location of the severe vibration of the vibrator, and the stiffness of the biasing strip. The loudspeaker of the present invention is made of a fiber-reinforced polymer composite material, and the fiber angle of each layer is determined by the reference coordinates of the flat plate. The 0 ° layer indicates that the fiber direction coincides with the reference axis, and the 90 ° layer indicates that the fiber direction is perpendicular to the reference axis. The material properties of the composite layer are represented by the ratio of elastic module to density, E1 / ρ and E2 / ρ. Among them, E1 and E2 are Young's moduli perpendicular to the fiber direction and the fiber direction, respectively, and ρ is the density of the material.

比 The ratio of the elastic module to the density has a significant effect on the natural mode parameters of the flat plate, the magnitude and distribution of the sound pressure sensitivity. In general, composite laminates having a relatively small elastic module-to-density ratio primarily produce sound pressure at relatively low frequencies (50 Hz to 500 Hz). In contrast, composite laminates having a relatively large elastic module-to-density ratio produce suitable sound pressure sensitivity in the mid-high frequency range (500 Hz to 20 KHz). Then, from the analysis of the sound pressure sensitivity of these one series, when a suitable high pressure sensitivity frequency spectrum is generated within the auditory frequency range of 50 Hz to 20 KHz, the ratio between the elastic module and the density of the composite is in the range of the following equation (4). It is understood that it is preferable to be limited to within.

（４）
　本考案の拡声用複合物積層板は例えば矩形とすることができ、その長さａ、幅ｂ、厚さｈにおいて、ｂの値はａ／４とａとの間にある。複合物積層板の積層方式は自然モードパラメータ例えば自然周波数、振幅及び振動型に対して重大な影響を及ぼすので、直接複合物積層板の拡声効果に影響する。積層方式において考慮されるパラメータは積層数と各層の繊維角度であり、一系列な拡声板音圧感度周波数スペクトルの分析から、最適な積層方式は例えば［０°／９０°／０°／・・・］ｓの直交性積層方式及び例えば［θ°／−θ°／θ°／・・・］ｓの対角交錯積層方式等であり、括弧外の下標示”ｓ”は対称積層を表示し、θは０°と ９０°との間に介在する角度である。なお、積層の層数は拡声板のサイズにより決定され、一般に、長さａが３０ｃｍよりも小さいか又は等しい場合、層数は１ないし３層、そして長さａが３０ｃｍよりも大きく５０ｃｍよりも小さい場合、層数は４層、長さａが５０ｃｍよりも大きいか又は等しい場合、層数は５層以上である。通常、長さａが５０ｃｍよりも大きい場合は拡声板をサンドイッチ方式に製造するのが好ましく、そのサンドイッチ式拡声板の層間の挟み材は材質が軽量の発泡材又はビーハイブ式心材を用いて製造することができる。

(4)
The sound-emitting composite laminate of the present invention may be, for example, rectangular, and the value of b is between a / 4 and a in length a, width b, and thickness h. The lamination scheme of the composite laminate has a significant effect on the natural mode parameters such as natural frequency, amplitude and vibration type, and thus directly affects the loudspeaker effect of the composite laminate. The parameters considered in the lamination method are the number of layers and the fiber angle of each layer. From an analysis of a series of sound pressure sensitivity frequency spectra of a loudspeaker, the optimum lamination method is, for example, [0 ° / 90 ° / 0 ° /. .] S orthogonal lamination system and, for example, [θ ° / −θ ° / θ ° /...] S diagonal cross lamination system, etc. , Θ are angles between 0 ° and 90 °. Note that the number of layers in the stack is determined by the size of the loudspeaker. Generally, when the length a is less than or equal to 30 cm, the number of layers is one to three, and the length a is greater than 30 cm and greater than 50 cm. If small, the number of layers is four, and if length a is greater than or equal to 50 cm, the number of layers is five or more. Usually, when the length a is larger than 50 cm, it is preferable to manufacture the loudspeaker in a sandwich system, and the sandwiching material between layers of the sandwich loudspeaker is manufactured using a lightweight foam material or a beehive-type core material. be able to.

The biasing strip added around the perimeter of the loudspeaker can be formed integrally with the flat plate, or can be attached to the edge of the flat plate with an adhesive. The cross section of the biasing strip is rectangular, but the stiffness of the biasing strip can be adjusted by changing its cross-sectional area. With respect to this rectangular loudspeaker, the vibration mode parameters of the loudspeaker can be adjusted using four biasing strips having different stiffnesses. A suitable sound pressure sensitivity spectrum can be generated within the frequency range. In analyzing the sound pressure sensitivity, an upper limit is set on the stiffness of the biasing strip to accelerate the convergence of the analysis, and this limit is achieved by controlling the cross-sectional area and Young's modulus of the biasing strip. Generally, the thickness of the biasing strip is less than three times the thickness of the plate, the width is less than one tenth of the width of the plate, and the Young's modulus is less than or equal to the fiber direction Young's modulus value of the plate. Must be set to In the sound pressure sensitivity frequency spectrum analysis, when the stiffness of the biasing strip on a certain side of the flat plate is zero, the side is not biased.

激 The vibrator that drives the loudspeaker to generate sound pressure can be divided into two types: an electromagnetic coil type and a piezoelectric type, which are similarly adhered to the surface of the loudspeaker by an adhesive method. Since the location of the tremor on the loudspeaker has a significant effect on the amplitude of each natural mode of the loudspeaker and the sound pressure sensitivity of the loudspeaker, different sonic sensitivity of the loudspeaker at different positions will cause different sound pressure sensitivities. appear. Usually, the surface of the loudspeaker is divided into both high- and low-efficiency loudspeaker regions, and the positions of these regions on the loudspeaker are determined by analyzing the sound pressure sensitivity frequency spectrum. In the analysis process, the stiffness of the biasing strip around the loudspeaker board was set to zero, and only one tremor point was considered, and several specific points were selected on both diagonal lines, horizontal and vertical lines passing through the center point of the loudspeaker. The high-pressure sensitivity spectra obtained from these specific points are analyzed, and the size and position of the high-efficiency loudspeaker region are determined by the internal difference method. Speaking of a rectangular plate having a length and a width of a and b, respectively, the high-efficiency loudspeaker region is also a rectangular region and is located in the middle of the plate. The length and width of this area are a / 4 and b / 4, respectively. Typically, the average sound pressure sensitivity obtained by trembling the loudspeaker in the high-efficiency loudspeaker region is at least 10 dB higher than that obtained in the low-efficiency loudspeaker region. The position set in the high-efficiency loudspeaker area of the tremor is determined according to the stiffness distribution of the biasing strip around the loudspeaker, in order to produce a more evenly distributed sound pressure sensitivity within a specific frequency range. Must. In general, the location of the shaker in the high-efficiency loudspeaker region and the stiffness of the biasing strip are determined by analyzing the sound pressure sensitivity frequency spectrum produced by the combination of the different shaker locations and the biasing strip stiffness due to the permutation method. You.

As described above, in order to design a high-efficiency composite laminate panel type loudspeaker, the ratio of the elastic module of the composite to the weight density appropriately used, the lamination method of the composite laminate (the number of layers and the fiber of each layer) are considered. Design parameters must be selected, including the angle (including angle), the stiffness of the biasing strip around the plate, and the location of a given number of seismic shakers in the high-efficiency loudspeaker area. Since the optimization method has already been widely applied and many process problems have been effectively solved, it is effective to design the composite laminate panel type speaker of the present invention by applying these optimization methods. The above-mentioned design parameters can be obtained. As another simple design method, a method of designing a composite laminate panel type speaker in a two-stage system has been adopted. That is, in the first stage, a composite laminate without an energizing strip is first designed, and an appropriate composite is analyzed by analyzing the sound pressure photometric frequency spectrum generated by vibrating the laminate in the high-efficiency loudspeaker region on the plate. And the lamination method (the number of laminations and the fiber angle) of the laminate. Then, in the second stage, the stiffness of the biasing strip around the plate and the position of a predetermined number of vibrators in the high-efficiency loudspeaker area are designed by a folding method or an optimization method.

FIG. 1 is a sketch showing the composite laminated panel type speaker of the present invention. In the figure, reference numeral 6 denotes a composite laminated panel type speaker, in which a length is a, a width is b, and a thickness is h, and b is smaller than a and larger than or equal to a / 4. A composite loudspeaker 7 is included. The composite loudspeaker 7 is composed of a composite laminate 40, a set of biasing strips 60, and at least one shaker 50. Around the periphery is still connected a flexible suspension system 20 fixed beside the frame 10 which does not deform easily. The suspension system 20 is made of a high-dumped foamed rubber strip, a wavy soft rubber-cotton cloth strip or a spider web-shaped plastic strip. In addition to suspending the loudspeaker 7, noise generated near the loudspeaker 7 is also reduced. It has a function to remove. The structure and characteristics of the composite laminate 40 including the loudspeaker and the biasing strip 60 formed around the back side thereof will be described in detail with reference to FIG. A high-efficiency loudspeaker area 30 is defined on the loudspeaker, its length and width are a / 4 and b / 4, respectively, and it is located in the central area of the loudspeaker. A tremor 50 on the loudspeaker is fixed in the high-efficiency loudspeaker area and drives the composite laminate to produce and generate vibration. The position of the vibrator 50 in the high-efficiency loudspeaker region is determined by the sound pressure sensitivity frequency spectrum analysis method proposed by the present invention. If the composite laminate is driven by only one shaker, the length a of the plate must be less than or equal to 40 cm. The vibrator 50 is connected to the current amplifier by two electric wires 56, and the magnitude of the thrust of the vibrator can be adjusted by controlling the amplification multiple of the current amplifier, so that the level of the sound pressure generated in the speaker can be controlled. Can be.

FIGS. 2 (a) and 2 (b) are diagrams showing an elastic suspension system 20 for suspending the loudspeaker plate 7, respectively. 2 (a) is a cross-sectional view of FIG. 1, in which the right side of the loudspeaker plate 7 is formed using a suspension system formed by using a foamed rubber strip 20a, and the left side is formed by using a wavy soft rubber-cotton cloth 20b. Suspended suspension system is provided. Each suspension system is fixed around the rectangular frame 10. On the other hand, FIG. 2B is an enlarged view of the lower corner portion of FIG. 1, in which the edge of the loudspeaker 7 and the web-like plastic suspension system 20c are connected to each other, and the other end of this suspension system is a rectangular frame 10 It is fixed around.

FIGS. 3A and 3B are cross-sectional side views in the length direction and the width direction of the speaker 6 in FIG. 1, respectively. FIG. 2 shows the loudspeaker board 7, the suspension system 20, and the frame 10. The loudspeaker 7 is composed of a three-layer composite laminate 40 and a pair of biasing strips 60, and the number of composite laminates and the stiffness of the biasing strip are determined according to the size of the loudspeaker. Is done. The material of the composite laminate is limited by Equation (4), the thickness of each composite layer is 0.1 mm to 0.2 mm, and the number of layers is determined by the size of the plate. Here, assuming that the length of the composite laminate is a and the number of layers is N, the number of layers is selected by the following equation.
When a ≦ 30 cm, N ≦ 3;
When a intervenes between 30 cm and 50 cm, N = 4:
When a ≧ 50 cm, N ≧ 5 (5)
For a large area loudspeaker, if a ≧ 50 cm, the optimal manufacturing method is to design a loudspeaker using a composite sandwich flat plate, use a composite laminate as a panel, and use a foam or beehive structure for the sandwich layer. used. The lamination method of the composite loudspeaker laminate is such that the fiber angles are symmetrically laminated using composite layers having 0 ° and 90 °, respectively, for example, [0 ° / 90 ° / 0 ° / ...] s There is a lamination method. The "s" marked in the lower right corner of the parentheses indicates that the laminate is a symmetric laminate. Another lamination method adopted is to alternately laminate composite layers having a fiber angle θ and −θ, for example, a method of [θ / −θ / θ /. In the formula, θ indicates an angle larger than 0 ° and smaller than 90 ° (0 ° <θ <90 °). The biasing strips 60 are secured to the edges of the composite laminate 40, and each biasing strip has a different stiffness. By changing the stiffness of the biasing strip, the natural mode parameters of the composite laminate 40 can be changed, so that the vibration type of the composite laminate of the biasing strip can be changed, and the plate surface has the opposite phase shift angle. The interference of sound pressure generated due to the presence of the region can be reduced, thereby obtaining a sound pressure sensitivity frequency spectrum relatively uniformly distributed and improving the facsimile effect of the loudspeaker. The features of the biasing strip are rectangular in cross section, the thickness is less than three times the thickness of the laminate, the width is less than one tenth of the laminate, and the Young's modulus is It must be equal to or less than the E1 value of the object. FIG. 3B is a cross-sectional side view taken along the line BB of FIG. 1, and biasing strips having different sizes are additionally formed on the edges of the composite laminate 40.

FIGS. 4 (a) and 4 (b) are diagrams showing electromagnetic coil type vibrators 50 having different current flow directions. In the figure, each vibrator 50 is composed of a permanent magnet 58, a conductive magnet 54 connected to both poles of two permanent magnets 58, and a coil winding 51. The ends of the magnets 54 form the north and south poles and produce a horizontal magnetic field between the two poles. The coil winding 51 includes a cylindrical coil 52 and an end cover 53 disposed on the top of the coil. The end cover 53 connects the vibrator 50 to the composite laminate 40 and connects to the soft support 55. By doing so, the coil 52 is concentrically arranged between the north and south poles of the conductive magnet. Therefore, when an electric current flows through the coil, it causes the coil to move vertically between the two conductive magnets 54. In FIG. 4 (a), when current flows through the connection point U on the left side of the shaker, it flows into the coil from top to bottom, and then flows out of the shaker through the connection point d on the right side. Such a flow direction in the current direction causes the coil 52 of the vibrator to move upward and generate an upward thrust. Also, in FIG. 4 (b), the flow direction of the current in the vibrator is just opposite to the flow direction in FIG. 4 (a), and the current flows from the bottom to the top of the coil. Accordingly, the coil is caused to perform a downward movement, thereby generating a downward thrust.

FIG. 5 is a view showing a state in which four intense vibrators 50 are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. In the figure, each of the two vibrators is divided into one set, the sets are connected in a parallel manner, and the two vibrators in each set are connected in a series manner. Assuming that the resistance of each one of the earthquake shakers is R, the resistance of the entire earthquake shaker circuit system also becomes R according to Ohm's law. The seismic devices are all located on the diagonal of the high-efficiency loudspeaker area, and on each diagonal there are two seismic devices located on both sides of the center point. The distance between each seismic device and the center point is determined by the present invention. Determined by the proposed sound pressure sensitivity frequency spectrum analysis method. In this case, if four intense vibrators are employed, it is preferable that the length a of the plate is smaller than 100 cm.

FIG. 6 is a view showing another practical example in which four intense vibrators 50 are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. As shown in FIG. 4A, the current flow direction in the three vibrators has the action of acting in the same direction as shown in FIG. The directions are opposite to the three current flow directions as shown in FIG. Divide the four tremors into two sets, there are two tremors in each set, the connection between sets is connected in parallel, and the two tremors in each set are connected in series Have been. The four intensifiers are respectively arranged on both diagonal lines in the high-efficiency loudspeaker area 30, have two intensifiers for each diagonal line, and are respectively located on both sides of the central point. The distance between each intensifier and the center of the high-efficiency loudspeaker region is determined by the sound pressure sensitivity frequency spectrum method proposed in the present invention. Among them, one attenuator having the opposing motion acts to eliminate the amplitude of the excessively shaken frequency or adjust the vibration type of the loudspeaker 7 to interfere with the opposite phase angle sound pressure on the plate surface. It acts as a main damper to reduce the power.

FIG. 7 is a view showing another practical example in which eight vibrators 50 are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. In the figure, the vibrators 50 are all arranged on specific lines (including two diagonals, one horizontal line, and one vertical line) passing through the center point of the high-efficiency loudspeaker area 30. That is, one strong shaker is arranged on each side of the center point of each specific line. The distance between the strong shaker and the center point in the high-efficiency loudspeaker region is determined by the sound pressure sensitivity frequency spectrum analysis method proposed in the present invention. Above all, as a preferable pattern for arranging the tremors, in a circle having a center at the center of a circle and a radius of b / 6 to b / 4, the tremors are arranged at the intersection of the circle and a specific line. The optimal radius of the circle is determined by the sound pressure sensitivity frequency spectrum analysis method proposed in the present invention. Also, the eight seismic shakers are divided into two sets, each set has four seismic shakers, the sets are connected in parallel with each other, and the seismic shakers in each set are connected in series. You. Assuming that the resistance of each vibrator is R, the resistance of the vibrator circuit system is 2R according to Ohm's law. When using eight intense vibrators, the length a of the loudspeaker 7 is preferably set between 100 cm and 200 cm.

FIG. 8 is a view showing another practical example in which eight vibrators 50 are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. Among them, the seven seismic devices have the same current flow direction as shown in FIG. 4 (a), so that the operation of the seismic devices is the same. As shown in FIG. 4 (b), the flow direction is opposite to that of the other seven seismic shakers, and therefore has an operation in the opposite direction. The anti-vibration device having the opposite operation acts to eliminate the amplitude of the excessively shaken frequency or adjust the vibration type of the loudspeaker plate 7 to reduce the interference between the opposite phase angle sound pressures on the plate surface. It works as a propulsion damper. Each of the eight intensifiers 50 is disposed on a specific line (including two diagonals, one horizontal line, and one vertical line) passing through the center point of the high-efficiency loudspeaker area 30. That is, one strong shaker is arranged on each side of the center point of each specific line. The distance between the strong shaker and the center point in the high-efficiency loudspeaker region is determined by the sound pressure sensitivity frequency spectrum analysis method proposed in the present invention. Above all, as a preferable pattern for arranging the tremors, in a circle having a center at the center of a circle and a radius of b / 6 to b / 4, seven tremors having the same operation act at the intersection of the circle and a specific line. Placed in And one seismic shaker with the other opposing action is located near the remaining unloaded intersection. The distance between the shaker and the center point and the optimum radius of the circle are determined by sound pressure sensitivity frequency spectrum analysis. Also, the eight seismic shakers are divided into two sets, each set has four seismic shakers, the sets are connected in parallel with each other, and the seismic shakers in each set are connected in series. ing. Therefore, if the resistance of each vibrator is R, the resistance of the vibrator circuit system is 2R.

FIG. 9 is a view showing another practical example in which sixteen vibrators 50 are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. In the figure, each seismic device is arranged on a specific line passing through the center point of the high-efficiency loudspeaker area 30. These specific lines are divided into two sets, the first set of specific lines includes a diagonal, one horizontal line, and one vertical line, and the second set of specific lines is composed of four other specific lines. Each line is a straight line of both included angles that are adjacent in the first set. One strong shaker is disposed on each side of the center point in each specific line, and the distance between the strong shaker and the center point is determined by the sound pressure sensitivity frequency spectrum analysis method proposed in the present invention. Among them, as a preferable pattern for arranging the seismic tremors, in two concentric circles having a center at the center and radii of b / 4 and b / 8, the great circle intersects the first set of lines with eight points, Meanwhile, the small circle intersects the second set of lines at eight points. The 16 tremors are divided into two sets of eight, and both sets are located at the intersection of both large and small circles. The pairs are connected in parallel with each other, and the seismic devices in each pair are connected in series. Accordingly, if the resistance of each seismic device is R, the resistance of the entire seismic device circuit system is also R. Further, as shown in FIG. 4 (a), all the vibrators have the same current flow direction, so that the operation of each vibrator is the same. In addition, when 16 seismic shakers are mounted on the board surface, it is preferable that the length a of the loudspeaker board 7 is set to be larger than 100 cm.

FIG. 10 is a view showing a state in which 16 intense vibrators 50 of another embodiment are arranged in the high-efficiency loudspeaker area 30 of the loudspeaker board 7. In the figure, out of the 16 seismic devices, fifteen seismic devices 50 have the same current flow direction as shown in FIG. 4 (a). However, as shown in FIG. 4B, the direction of current flow in the sixteenth seismic shaker is opposite to that of the other fifteenth seismic shakers, so that it has an operation in the opposite direction. The anti-vibration device having the opposite operation acts to eliminate the excessively shaken frequency amplitude or adjust the vibration type of the loudspeaker plate 7 to reduce the interference between the opposite phase angle sound pressures on the plate surface. It works as a driven damper. The 16 seismic shakers are divided into two sets of eight each, the sets being connected in parallel, and the shakers in each set being connected in series. Therefore, if the resistance of each seismic device is R, the resistance of the entire seismic device circuit system is also R. Each vibrator is arranged on a specific line passing through the center point of the high-efficiency loudspeaker area 30. These specific lines are divided into two sets, the first set of specific lines includes bi-diagonal lines, one horizontal line and one vertical line, and the second set of specific lines is composed of four other specific lines, Each of the lines is a straight line of both included angles that are adjacent in the first set. One strong shaker is disposed on each side of the center point in each specific line, and the distance between the strong shaker and the center point is determined by the sound pressure sensitivity frequency spectrum analysis method proposed in the present invention. Among them, as a preferred pattern for arranging the seismic devices, in two concentric circles with the center point as the center of the circle and the radii of b / 4 and b / 8, the great circle intersects the first set of lines with eight points. While the small circle intersects the second set of lines with another eight points. In both sets, the seismic tremor having the same operation is arranged at the intersection of the great circle and the small circle, and the seismic tremor having the operation in the opposite direction is arranged near the intersection of the great circle and one diagonal line. Have been. The distance between the shaker and the center point is determined by high pressure luminous frequency spectrum analysis. The mounting pattern of the main damper using the seismic shaker having two or more opposing operating actions can be determined based on the above method.

FIG. 1 is a schematic view showing a composite laminated panel type speaker of the present invention. FIG. 2A is a cross-sectional view of FIG. 1 in which the suspension systems on both the left and right sides of the panel-type speaker are respectively formed using a foamed rubber strip and a wavy soft rubber-cotton cloth. FIG. 2B is a partially enlarged view of FIG. 1, which is a flexible spider-like plastic body for hanging a loudspeaker. FIG. 3A is a sectional view taken along the line AA in FIG. FIG. 3B is a sectional view taken along line BB in FIG. FIG. 4 (a) is a diagram illustrating an electromagnetic coil type vibrator in which a current flows from the top to the bottom of the coil to move the coil upward and generate an upward thrust. FIG. 4 (b) is a diagram showing an electromagnetic coil type vibrator in which a current flows from the bottom to the top of the coil to move the coil downward and generate a thrust downward. FIG. 5 is a diagram showing a state in which four electromagnetic coil type vibrators are arranged in a high-efficiency loudspeaker area of a loudspeaker board. FIG. 6 is a view showing a state in which four electromagnetic coil type vibrators according to another embodiment are arranged in a high-efficiency loudspeaker area of a loudspeaker. FIG. 7 is a view showing a state in which eight electromagnetic coil type vibrators according to another embodiment are arranged in a high-efficiency loudspeaker area of a loudspeaker. FIG. 8 is a view showing a state where eight intense vibrators according to another embodiment are arranged in a high-efficiency loudspeaker area of a loudspeaker board. FIG. 9 is a view showing a state in which 16 intense vibrators according to another embodiment are arranged in a high-efficiency loudspeaker area of a loudspeaker. FIG. 10 is a view showing a state in which sixteen vibrators according to another embodiment are arranged in a high-efficiency loudspeaker area of a loudspeaker board.

Explanation of reference numerals

Reference Signs List 6 Speaker 7 Speaker board 10 Rectangular frame 20 Spider-like plastic suspension system 30 High-efficiency speaker area 40 Composite laminate 50 Strong vibration Device 56: electric wire 60: urging strip

Claims (5)

A panel-type speaker that raises its voice due to the occurrence of flexible vibration,
A rectangular composite laminate having a length a, a width b, and an additional biasing strip formed around the periphery;
At least one vibrator fixed on said composite laminate and vibrating said composite laminate to generate a flexible vibration thereto;
A panel-type speaker, comprising: a high-efficiency loudspeaker area located on a surface of the composite laminate and violently blasting the composite laminate by the vibrator to generate relatively high sound pressure sensitivity. The composite laminate in the panel speaker is a rectangular plate set so that width b is smaller than or equal to length a and b is larger than a / 4,
The composite laminate is composed of a composite layer having a specific number and orthogonal materials, wherein the thickness of each composite layer is between 0.1 and 0.2 mm, and its Young's modulus and density are Is between 80 and 80 GPa / (g / cm ³ ) in the fiber direction, between 3 and 10 GPa / (g / cm ³ ) in the substrate direction,
3. The speaker according to claim 2, wherein the composite material layer having the orthogonal material is made of a material such as a carbon fiber reinforced epoxy resin, a glass fiber reinforced epoxy resin, or a boron fiber reinforced epoxy. The composite laminate used for the panel loudspeaker is obtained by laminating two kinds of composite layers having a center plane of the laminate as a plane of symmetry, that is, a composite layer having a fiber angle of 0 ° and 90 ° in a symmetrical manner. And a lamination method in which composite layers having a fiber angle of θ (0 ° <θ <90 °) and −θ are laminated in a symmetric manner.
The number of laminations contained in the composite laminate plate is determined according to the length a of the plate. If a is within 30 cm, the number of laminations is 3 or less, and if a is between 30 cm and 50 cm, the number of layers is The speaker according to claim 1, wherein the number of layers is four, and if a is greater than 50 cm, the number of layers is at least five. In the panel-type speaker, four biasing strips having different rigidities are additionally formed around the rectangular composite laminate, and the thickness of each biasing strip is the thickness of the composite laminate. Less than three times the width of the composite laminate, the width being less than one-tenth of the width of the composite laminate, and the Young's modulus of each biasing strip being less than or equal to the Young's modulus in the fiber direction of the composite. Is set,
The biasing strip in the panel type speaker has a function of suppressing a standing wave staying on the composite laminate edge and adjusting a natural vibration mode of the composite laminate, By selecting a more suitable biasing strip stiffness to reduce the generation of noise and generating a vibration type that contributes to the sound increase in the composite laminate, the sound generated from the region of the laminate surface in the non-uniform movement direction. The loudspeaker of claim 1, wherein pressure interference is reduced. The speaker according to claim 1, wherein the vibrator for vibrating the composite laminate is an electromagnetic coil type or a piezoelectric vibrator.

Images