TW462201B - Acoustic device - Google Patents
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- TW462201B TW462201B TW088105770A TW88105770A TW462201B TW 462201 B TW462201 B TW 462201B TW 088105770 A TW088105770 A TW 088105770A TW 88105770 A TW88105770 A TW 88105770A TW 462201 B TW462201 B TW 462201B
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Classifications
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
- H04R7/00—Diaphragms for electromechanical transducers; Cones
- H04R7/02—Diaphragms for electromechanical transducers; Cones characterised by the construction
- H04R7/04—Plane diaphragms
- H04R7/045—Plane diaphragms using the distributed mode principle, i.e. whereby the acoustic radiation is emanated from uniformly distributed free bending wave vibration induced in a stiff panel and not from pistonic motion
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
- H04R1/00—Details of transducers, loudspeakers or microphones
- H04R1/20—Arrangements for obtaining desired frequency or directional characteristics
- H04R1/22—Arrangements for obtaining desired frequency or directional characteristics for obtaining desired frequency characteristic only
- H04R1/24—Structural combinations of separate transducers or of two parts of the same transducer and responsive respectively to two or more frequency ranges
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- Engineering & Computer Science (AREA)
- Signal Processing (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Otolaryngology (AREA)
- Health & Medical Sciences (AREA)
- Multimedia (AREA)
- Details Of Audible-Bandwidth Transducers (AREA)
- Diaphragms For Electromechanical Transducers (AREA)
- Obtaining Desirable Characteristics In Audible-Bandwidth Transducers (AREA)
- Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
- Piezo-Electric Transducers For Audible Bands (AREA)
- Fittings On The Vehicle Exterior For Carrying Loads, And Devices For Holding Or Mounting Articles (AREA)
Abstract
Description
4 6 2 20 1 五、發明說明(1) 技術領域 本發明係關於音響裝置,更特別但卻非單獨的是,係關 於加入有諧振多模諧振壁音響輻射體的揚聲器,例如,我 們的國際專利申請案W 0 9 7 / 0 9 8 4 2號中所說明的種類是也。 W097/0 9 842中所說明的揚聲器已成為通稱的分佈模(DM)揚 聲器。 一般而言,均係將分佈模揚聲器(DML )與稀薄,輕巧而 扁平的諧振壁相結合,此等面壁均係以一種複數擴散方式 等量地輻射來自各側面的聲能。雖然這是分佈模揚聲器之 一項有用特性,但卻具有各種現實世界的狀況,在這些狀 況中,由於此種應用及其邊界需求採會愛用一種分佈模揚 聲器的單極形式。 在這些應用中,此種具有優點的產品可能為輕巧,稀薄 不易受人注意。 背景技術 從國際專利申請案W 0 9 7 / 0 9 8 4 2號大家都知道係將一多模 諧振音響輻射體安裝在一個比較淺薄的密封箱内,因而, 才會圍堵來自該輻射體之一個表面的音響輻射。在這方面 所應注意的,在本文中的”淺薄M —詞乃係關於一個活塞錐 型揚聲器驅動單元在一有效容積封閉體内的典型比例。一 項典型的容積與活塞隔膜面積比可能為以毫升(m 1 )對平方 公分(c m2)表示的8 0 : 1 。一個諧振壁揚聲器用的淺薄封閉 體可能具有2 0 : 1的比值,在那裡一處集總空氣容積的活塞 式驅動卻很少關連。4 6 2 20 1 V. Description of the Invention (1) Technical Field The present invention relates to a sound device, and more particularly, but not exclusively, to a speaker incorporating a resonant multi-mode resonance wall acoustic radiator, for example, our international The type described in Patent Application No. W 0 9 7/0 9 8 4 2 is also. The speaker described in W097 / 0 9 842 has become known as a distributed mode (DM) speaker. Generally speaking, they all use a distributed mode loudspeaker (DML) combined with a thin, lightweight and flat resonant wall. These surface walls radiate the sound energy from each side in an equal amount in a complex diffusion manner. Although this is a useful feature of distributed mode loudspeakers, it has a variety of real-world conditions in which, due to this application and its boundary requirements, a unipolar form of distributed mode loudspeaker is preferred. In these applications, such advantageous products may be lightweight and thin and not easily noticeable. BACKGROUND From the international patent application No. W 0 7 7/0 9 8 4 2 it is known that a multi-mode resonant acoustic radiator is installed in a relatively shallow sealed box, so that the radiator from the radiator is enclosed. Acoustic radiation from one surface. It should be noted in this regard that the term "shallow M-" in this article refers to a typical ratio of a piston cone speaker drive unit in an effective volume enclosed body. A typical volume to piston diaphragm area ratio may be 80: 1 expressed in milliliters (m1) versus square centimeters (cm2). A shallow enclosure for a resonant wall speaker may have a ratio of 20: 1, where there is a piston-type drive that lumps the air volume But rarely related.
4 6 2 20 1 五、發明說明(2) 發明說明 根據本發明,音響裝置由具有對立表面之一諧振多模音 響諧振器或輻射體壁及界定一空腔的裝置組成,該空腔封 閉一處壁面的至少一部並被配置來圍堵來自該壁面部分的 音響輻射,其中此空腔為如此方式,俾修正此輻射體壁之 模式行為表現。空腔被密封起來。可配置一震動激發器, 以便由曲線波震動施加至諧振壁,以產生音響輸出,因 而,使裝置的功能作用為揚聲器。 其空腔大小可為如此方式,俾修正諧振壁之模式行為表 現。 此空腔可能是淺薄的。它可能足夠淺薄,以致使鄰近此 一壁面之内腔面與此其壁面之間的距離充分微小,因而造 成與此諧振壁的流體耦合。空腔内之諧振模式可由與諧振 壁平行的正交模(亦即,沿著諧振壁調變的模式)及與諧振 壁成直角的垂直模組成。就愛用方式言,空腔均充分淺 薄,因而,在修正諧振壁的模式時,正交模(X, Y )比垂直 模(Z)更為顯著。在各具體實例中,垂直模的頻率均可在 重要頻率範圍以外。 空腔容積與諧振壁之比率(m 1 : cm2)可小於1 0 : 1 ,例如, 在大約1 0 : 1至0 . 2 : 1的範圍内。 諧振壁可由——般為傳統式彈性週邊予以終止在其邊緣 處。此周邊可似一傳統式活塞驅動單元的滾形周邊並可由 一條或多條波紋組成。此種彈性週邊可由發泡橡膠條片組 成。4 6 2 20 1 V. Description of the invention (2) Description of the invention According to the present invention, an acoustic device is composed of a resonant multi-mode acoustic resonator or radiator wall having an opposite surface and a device defining a cavity, the cavity being closed in one place At least a portion of the wall surface is configured to block acoustic radiation from the wall surface portion, wherein the cavity is in such a manner as to modify the mode behavior of the radiator body wall. The cavity is sealed. A vibration exciter may be configured so that a curved wave vibration is applied to the resonance wall to generate an acoustic output, so that the device functions as a speaker. The cavity size can be such that the mode behavior of the resonant wall is modified. This cavity may be shallow. It may be shallow enough so that the distance between the cavity surface adjacent to this wall surface and its wall surface is sufficiently small, thus creating a fluid coupling with this resonant wall. The resonance mode in the cavity can be composed of an orthogonal mode parallel to the resonance wall (that is, a mode modulated along the resonance wall) and a vertical mode perpendicular to the resonance wall. In terms of favorite methods, the cavities are sufficiently shallow. Therefore, the orthogonal mode (X, Y) is more prominent than the vertical mode (Z) when modifying the mode of the resonance wall. In each specific example, the frequency of the vertical mode can be outside the important frequency range. The ratio of the volume of the cavity to the resonance wall (m 1: cm 2) may be less than 10: 1, for example, in a range of approximately 10: 1 to 0.2: 1. The resonant wall can be terminated at its edges by a generally elastic perimeter. This perimeter may resemble the rolling perimeter of a conventional piston drive unit and may consist of one or more corrugations. Such an elastic periphery may be composed of a foamed rubber strip.
第6頁 462201 五、發明說明(3) 就變換方式言’可將此错振壁的邊緣夾在封閉體内,例 如,和我們1 99 9年4月9曰所提出的共同待命pcT專利權 請案PCT/GB9 9/0 04 04號中所說明的一樣。 可將此種封閉體視為一淺盤,此淺盤含有—種流體,並 可將此種流體表面視為擁有似波浪的功能表現以及$特定 特性則視此種流體(空氣)與其體積或容積箱的幾何形狀^ 者而定。將此諧振壁安放成與此作用波面呈耦合接觸以及 由該譜振壁之表面波激勵來激發流體。反之,流體的自然 波特性與错振壁互動,因而’修正其功能行為表現。這是 本發明領域中具有新穎音響特性的一種複式耦合系統。 自另一項特色言,本發明係關於修正諧振壁音響裝置的 Ϊ ί行為Ϊ 5的方④’包括促使諧振壁與一邊界丄:成為 緊郴’以界疋它們之間的諸振空腔。 1„式_之簡單說明 圖 圖1為密封箱諧振壁揚聲器之第一具體實例之橫斷面 曲線圖 圖2為達-種放大比例之圖i具體實例的橫斷面^ 圖3為密封箱諧振壁之第二具體實例的橫斷面圖。 圖4表示雙側面上自㈣射之分饰模揚聲 圖5表示自由空間内之聲壓水平(實線)與配置離壁部35 厘米之分佈模揚聲器(DML)(虛線)之間的比較。 圖6表不自由空間内之分佈模揚聲器的音 前後部之間的壁部周圍之反射面的比較。力旱(i泉與Page 6 462201 V. Description of the invention (3) Regarding the conversion method, 'the edge of this staggered wall can be sandwiched in a closed body, for example, with our common standby pcT patent right proposed on April 9, 1999 The same is stated in the case PCT / GB9 9/0 04 04. Such a closed body can be regarded as a shallow plate, which contains a fluid, and the surface of the fluid can be regarded as having a wave-like functional performance, and the specific characteristics depend on the fluid (air) and its volume or The geometry of the tank is determined by ^. This resonant wall is placed in coupling contact with this wave surface and excited by a surface wave of the spectral wall to excite the fluid. Conversely, the natural wave characteristics of the fluid interact with the staggered wall, and thus ‘correct its functional behavior. This is a duplex coupling system with novel acoustic characteristics in the field of the present invention. According to another characteristic statement, the present invention is related to the modification of the resonance wall acoustic device. The 5th aspect of the invention includes the promotion of the resonance wall and a boundary 丄: becoming tight 郴 to limit the vibration cavities between them. . Brief description of the formula "1" Figure 1 is a cross-sectional curve diagram of the first specific example of the sealed box resonance wall speaker Figure 2 is a cross-section of a specific example of the figure of an enlarged scale i Figure 3 is a sealed box A cross-sectional view of a second specific example of the resonant wall. Figure 4 shows the self-ejecting decorative mold speaker on both sides. Figure 5 shows the sound pressure level (solid line) in free space and the distance 35 cm from the wall. Comparison between distributed mode speakers (DML) (dotted line). Figure 6 shows the comparison of the reflective surface around the wall between the front and back of the distributed mode speaker in a free space.
$ 7•頁 4 6 2 20 1 五、發明說明(4) 圖7表示根據本發明之揚聲器= 圖8表示一種分佈模揚聲器諧振壁系統。 圖9例示各組件的耦|合。 圖1 0例示一單壁特性函數。 圖11表示首先1 0個真空内諧振壁模式之頻率響應規模。 圖1 2表示根據本發明之具體實例之揚聲器内相同模式的 頻率響應規模。 圖1 3表示封閉物對壁速頻譜的效應。 圖1 4例示兩種模式形狀。 圖1 5表示電抗的頻率響應。 圖1 6例示壁速測量。 圖1 7例示供測量用的微音農置。 圖1 8表示不同壁部的機械阻抗。 圖1 9表示不同壁部的功率響應。 圖2 0表示不同壁部的極性反應。 圖2 1表示用以測量封閉物内部壓力的微音裝置。 圖22表示内部壓力輪廓。 圖2 3表示利用圖2 1陣列所測量之内部壓力。 圖24表示不同壁部的速度及位移。 圖2 5表示自由空間與封閉物内之A 5壁部的速率頻譜。 圖2 6表示自由空間與封閉物内之另一 A 5壁部的速率頻 譜。 圖2 7表示一種雙深度封閉物内之A 2壁部的功率響應。 圖2 8例示採用濾波器之等化。$ 7 • Page 4 6 2 20 1 V. Description of the invention (4) Figure 7 shows a loudspeaker according to the invention = Figure 8 shows a distributed mode loudspeaker resonance wall system. FIG. 9 illustrates the coupling of the components. FIG. 10 illustrates a single-wall characteristic function. FIG. 11 shows the frequency response scale of the first 10 vacuum internal resonance wall modes. Fig. 12 shows the frequency response scale of the same mode in a speaker according to a specific example of the present invention. Figure 13 shows the effect of the closure on the wall velocity spectrum. Figure 14 illustrates two pattern shapes. Figure 15 shows the frequency response of the reactance. Figure 16 illustrates wall speed measurement. Figure 17 illustrates a microphone farm for measurement. Figure 18 shows the mechanical impedance of different wall sections. Figure 19 shows the power response of different wall sections. Figure 20 shows the polar response of different wall sections. Figure 21 shows a microphonic device for measuring the internal pressure of a closure. Figure 22 shows the internal pressure profile. Figure 23 shows the internal pressure measured using the array of Figure 21. Fig. 24 shows the speed and displacement of different wall portions. Figure 2 5 shows the velocity spectrum of the A 5 wall in free space and in the enclosure. Figure 26 shows the velocity spectrum of another A5 wall in free space and in the enclosure. Figure 27 shows the power response of the A 2 wall in a double-depth enclosure. Figure 28 illustrates equalization using a filter.
第8賓 ιχ ό it » Πη n i _案號88105770 年/月(?曰 修正__ 五、發明說明(5) 在此等圖式中並更特別參照圖1及2時,密封箱揚聲器1 由W 0 9 7 / 0 9 8 4 2號申請案中所述種類之一諧振形音響輻射體 5在其前端處所封閉的箱形封閉物2組成。輻射體5被一震 動激發器4所授能且被一彈性懸吊6密封至圍繞其周邊的封 閉物。懸吊6係由例如個別人形部分之框架構件9,1 0内所 安置的發泡橡膠之對立彈性條片7組成,此等框架構件係 被扣件1 1所保持一起的,以形成框架8。封閉物2之後壁3 的内部表面1 4則製有硬化筋條1 2,以使後壁震動減至最 少。此種封閉物可為加入有此種硬化筋條的塑膠模製品或 鑄造品。 本具體實例中之諧振壁可為A 2尺寸以及空腔1 3的深度可 為9 0厘米。 圖3之揚聲器具體實例,一般而言,與圖1及2之具體實 例相同,但這裡卻係將輻射體壁5安裝於***在輻射體5邊 緣與密封空腔的封閉物之間例如發泡橡膠之一單獨彈性條 片懸吊6上。該項輻射體壁尺寸可為A5及其滦度可在3或4 厘米左右。 應知雖然圖1至3的具體實例係關於揚聲器者,但它卻同 樣可利用圖1至3的一般類別裝置生產一音響諧振壁,用以 修正一處空間(例如會客室或大禮堂)的音響行為表現,但 這裡卻省去震動激發器4的說明。 圖中所表示的,為此種配置形式的諧振壁,與活塞揚聲 器相比時,能以隔膜尺寸為準的極小封閉容積提供一項非 常有用的頻帶寬。茲特查驗負責此種界限與分佈模作用之No. 8 it »Πη ni _ Case No. 88105770 (/? Amendment __ V. Description of the invention (5) In these drawings and more particularly with reference to Figures 1 and 2, the sealed box speaker 1 consists of W 0 9 7/0 9 8 4 One of the types described in the application No. 2 is a box-shaped closure 2 in which the resonant acoustic radiator 5 is closed at its front end. The radiator 5 is energized by a vibration exciter 4 It is sealed to an enclosure around its periphery by an elastic suspension 6. The suspension 6 is composed of, for example, opposed elastic strips 7 of foamed rubber placed in frame members 9, 10 of individual humanoid parts, and these frames The components are held together by the fasteners 11 to form the frame 8. The inner surface 14 of the wall 3 behind the closure 2 is made of hardened ribs 12 to minimize the vibration of the rear wall. Such closures It can be a plastic molded product or a casting with this hardened rib. The resonant wall in this specific example can be A 2 size and the depth of the cavity 13 can be 90 cm. The specific example of the speaker in Figure 3 is general In terms of the same as the specific examples of Figs. 1 and 2, but here the radiator wall 5 is installed in the Between the edge of the projectile 5 and the sealing of the cavity, for example, a single elastic strip is suspended from a foam rubber 6. The size of the radiator wall can be A5 and its degree can be about 3 or 4 cm. It is known that although the specific examples of Figs. 1 to 3 are about speakers, it can also use the general type of devices of Figs. 1 to 3 to produce an acoustic resonance wall to modify the sound of a space (such as a reception room or auditorium). Performance, but the description of the vibration exciter 4 is omitted here. As shown in the figure, when compared with the piston speaker, the resonance wall of this configuration can provide an item with a very small closed volume based on the size of the diaphragm. Very useful frequency bandwidth. The Zitter test is responsible for the role of such bounds and distributed modes.
O:\57\57900.ptc 第9頁 2001.07. 05.009 462201 五、發明說明(6) 最小互動的機構以及圖中所進一步表示的,那就是總而言 之,一種簡單無源等他網路可能為產生一平坦功率響應曲 線所需要的全部。所亦經證明的,為在此項表示中,一具 :分佈模揚聲器能在其工作頻率範圍内將一種近乎理想的半 '球形方向性圖案產生成一處2 .7Γ _空間。 茲提出一種封閉形式的解決方法,此種方法為就此種諧 丨振壁與封閉物組合的辆合系統解答曲線波方程式的結果。 :求得此種系統的音響阻抗函數並順次予以用來計算此種耦 合封閉物對特性頻率的效應,以及預測對屏極模式的相關 轉移和增加量。 調查改變集總參數和大小之若干樣品的實驗性測量資料 ;並將這些測量數與來自分析模式的結果比較。 圖4例示一具自由分佈模揚聲器的典型極性響應。注 丨意,諧振壁平面内之壓力減小係因其邊緣處或附近之音響 丨輻射的抵銷效應所致。當將一具分佈模揚聲器接近與邊界 i表面成特別並行的一處邊界時,於將相去該表面之距離, !就大約5 0 0平方公分表面面積之諸振壁言,予以減小至低 |於大約1 5公分時,音響干擾方面始發生。其效應依其嚴重 1度及性質隨著距邊界的距離以及壁部大小而改變。無論如 何,其結果均以不變方式為低頻延伸的縮小,底部中間範 丨圍區内之響應曲線尖化,以及中間範圍及底部頻率三倍音 丨區内之某些像差,和圖5實例中的表示情形一樣。由於此 ;峯的緣故,不論可易於補償尖峯的事實怎樣,都會使一具 丨:”自由"分佈模揚聲器接近一處邊界的應用變為很受限制。O: \ 57 \ 57900.ptc Page 9 2001.07. 05.009 462201 V. Description of the invention (6) The mechanism with the least interaction and further shown in the figure, that is to say, in short, a simple passive network waiting for others may generate a All you need for a flat power response curve. It has also been proven that, in this representation, a: distributed mode loudspeaker can generate a nearly ideal hemispherical directional pattern into a 2.7 space in its operating frequency range. A closed-form solution is proposed. This method is the result of solving the curve-wave equation for such a hybrid system with a combination of vibration walls and closures. : Obtain the acoustic impedance function of this system and use it in order to calculate the effect of this coupling closure on the characteristic frequency, and predict the relevant transition and increase of the screen mode. Investigate experimental measurements of several samples that change lumped parameters and sizes; compare these measurements with results from analysis mode. Figure 4 illustrates the typical polar response of a free-distribution mode speaker. Note that the reduction in pressure in the plane of the resonant wall is due to the offsetting effect of acoustic radiation at or near its edges. When a distributed mode loudspeaker is approached to a boundary that is particularly parallel to the surface of boundary i, the distance from which the surface is phased out, is reduced to low by about 500 square centimeters of surface area. | At about 15 cm, acoustic interference began to occur. Its effect varies according to its severity 1 degree and the nature of the distance from the boundary and the size of the wall. In any case, the result is a constant reduction of low-frequency extension, a sharpened response curve in the bottom middle range, and some aberrations in the middle range and bottom frequency triples, as shown in the example in Figure 5. Representation is the same in. Because of this peak, regardless of the fact that it is easy to compensate for the spikes, the application of a "free" distributed mode speaker close to a boundary becomes very limited.
第10頁 4 6 2 20 I五、發明說明(7)' 丨 當將一分佈模揚聲器安放在一封閉箱或所謂約大容積之 i π無限反射面”内時,才會圍堵因壁部後方而起之輻射且一 1般而言拿在其中間及低頻響應曲線内加大前方的輻射,此 !等利益均來自兩項特色。第一係因缺乏干擾影響而起,此 ;等干擾效應係由在其空氣t之音響波長可以來自由壁空間 ;的頻率時前後方輻射所造成.;第二則係來自因反射面及輻 I射均在2ττ空間内之中間至低頻邊界強化的緣故,見圖6。 丨這裡,我們可以看出,用一處0,25平方公分表面面積的諧 |振壁才會達成1 0 0赫時之大約2 0分貝強化。 j 雖然這是使頻帶寬達到最大時之一項肯定優點,但是, [它可能實際上並非可以加入,除非此種應用本身對該項解 |決方法有用。各項適合的應用包含平頂揚聲器及定製壁内 丨設施。 f ! 在各種其他應用中,採用此種"無限反射面11結構造型可 !能具有肯定優點而設有諧振壁後大量封閉空氣容積的奢 |侈。這些應用亦可從揚聲器之全般薄度和輕巧獲得好處。 |本發明之目的為對此種形式的配置獲致了解並提供分析性 I解決方法。 大量工作均在支援各種操作模式中的傳統式活塞揚聲 器,特別是在當用於一封閉體内時預測其低頻行為表現方 面。值得一提的是,分佈模揚聲器均為非常新近的發展, 因此,幾乎沒有涉及該等問題的先前知識,以便有助於取 得有關類似分析的解決方法。在下面所跟著的說明中,乃 係採用一種途徑,此種途徑則係對包括裝載有一細小封閉Page 10 4 6 2 20 I. 5. Description of the invention (7) '丨 The wall will only be blocked when a distributed mode speaker is placed in a closed box or so-called i π infinite reflection surface with a large volume. Radiation from the rear and generally increase the radiation in the front in the middle and low-frequency response curve, these benefits come from two characteristics. The first is due to the lack of interference, and so on; The effect is caused by the front and rear radiation at the frequency of the acoustic wavelength of the air t which can come from the wall space; the second comes from the enhancement of the reflection surface and the radiation I from the middle to the low frequency boundary in the 2ττ space For the sake of illustration, see Figure 6. 丨 Here, we can see that using a harmonic surface with a surface area of 0,25 square centimeters, the vibration wall will reach about 20 dB at 100 Hz. Although this is the frequency A positive benefit when bandwidth is at its maximum, but [it may not actually be added unless the application itself is useful for the solution. Suitable applications include flat-top speakers and custom built-in walls. F! In various other applications, This " infinite reflection surface 11 structure can be shaped! It can have the luxury of luxury with a closed volume of air behind the resonance wall. These applications can also benefit from the thinness and lightness of the speaker. | The goal is to gain an understanding of this form of configuration and provide analytical solutions. A lot of work has been done to support traditional piston speakers in various modes of operation, especially in predicting low-frequency behavior when used in a closed body. It is worth mentioning that distributed mode speakers are very recent developments, so there is little prior knowledge of these issues in order to help obtain solutions for similar analysis. In the description that follows, A method is adopted, which is a small closure to the load
第U頁 462201 丨五、發明說明(8) |體的各種機械音響接面情況中所配置的分佈模揚聲器提供 i 一組有用的解決方法。 ! 茲將此種分析下的系統以示意圖方式表示在圖7中。在 此實例中,諧振臂的正側面乃係輻射在自由空間内,而其 其他側面則裝有一封閉體。可將此種耦合系統視作為一種 速度及壓力網路和圖8中所表示的情形一樣。各項組件均 I ' I係自左至右;電機驅動部分,諧振壁之模式系統,以及音 i響系統。 ! 一震動壁上面之曲波電磁場的速率乃係負責其音響輻 ί |射。此種輻射順次引起修正諧振壁震動的電抗力。如係從 i兩個側面等量輻射的分佈模揚聲器案例,則為電抗元件的 I輻射阻抗,與諧振壁之機械阻抗比較時,通常均不顯著。 然而,當此諧振壁輻射在二細小封閉體内時,音響阻抗因 其後方輻射而起的效應就會不再微小,並且事實上,對該 j讀振壁形態的比例它卻會修正和增加。Page U 462201 丨 V. Description of the invention (8) The distributed mode speakers provided in the case of various mechanical and acoustic interfaces provide a set of useful solutions. ! The system under this analysis is shown diagrammatically in Figure 7. In this example, the front side of the resonant arm is radiated in free space, while the other side is equipped with a closed body. This coupling system can be viewed as a speed and pressure network as in the case shown in Figure 8. All components are I'I from left to right; motor drive part, mode system of resonance wall, and sound system. ! The velocity of a curved wave electromagnetic field above a vibrating wall is responsible for its acoustic radiation. Such radiation sequentially causes a reactive force that corrects the vibration of the resonance wall. In the case of a distributed-mode loudspeaker that radiates equally from both sides of i, it is the I radiation impedance of the reactive element, which is usually not significant when compared with the mechanical impedance of the resonance wall. However, when this resonance wall radiates in two small enclosed bodies, the effect of acoustic impedance due to the radiation behind it will no longer be small, and in fact, it will modify and increase the proportion of the j-reading wall shape. .
I 根據圖9的表示,此種耦合相當於一種機械音響封閉環 i |路系統,在此系統中,其電抗聲壓係因諧振壁之速度本身 !而起。此項壓力會修正變曲波電磁場的模式分佈,此舉順 |次對聲壓反應及諧振壁的方向性具有影響。 丨 為求計算方向性並檢查此種系統内部的作用力和流路 |計,必須解決屏極速率的問題。而後,才能借助此種速率 的F 〇 u r i e r變換求得此種遠場聲壓響應,和P A N Z E R, J ; HARRIS, N ;所著論文中所說明的一樣,其名稱為”分佈模 揚聲器輻射模擬”,該論文係在舊金山市1 9 9 8年的第10 5屆I According to the representation in Figure 9, this coupling is equivalent to a mechanical acoustic closed-loop i | road system, in which the reactive sound pressure is caused by the velocity of the resonance wall itself. This pressure will modify the mode distribution of the variable curve electromagnetic field, which in turn has an effect on the sound pressure response and the directionality of the resonant wall.丨 In order to calculate the directivity and check the internal force and flow path of such a system, the problem of the screen speed must be solved. Then, this far-field sound pressure response can be obtained by using the Fourier transform at this rate, which is the same as that described in PANZER, J; HARRIS, N; , The dissertation was in the 105th edition of San Francisco in 1988
第12頁 4 6 2 201 五、發明說明(9) AES會議中提出的編號為4783。因此,才能借助網路分析 求得該等作用力和流路·>可接達此項問題的方法為依據 CREMER,L; HECKL,Μ; UNGAR,E ;所著 1 973 年的 ^ SPRINGER"結構體出生的聲音以及BLEVINS, R. D.所著、Page 12 4 6 2 201 V. Description of Invention (9) The number proposed in the AES meeting is 4783. Therefore, it is possible to obtain such forces and flow paths through network analysis. ≫ The approach to this problem is based on CREMER, L; HECKL, M; UNGAR, E; ^ SPRINGER " 1973 Structure-born sounds and BLEVINS, RD,
1984年KRIEGER. Publ., MALABAR"自然頻率及模式形狀A 式11等中所說明之真空内諧振壁特性函數(3,4 )來崖生& .^ % it 種全部系統之速率及壓力。例如,可自方程式(1) st开 振壁上任何點處的速率。 c〇 /⑽)= Σ Ypiij^) ' F〇i(it〇) * ^pi(x〇.y〇) ' ^pi(x.y) (1) 當予以耦合至電機集總元件網路及其立即音響邊界時’ 此種系列代表對於說明屏極曲線波之微分方程式的一種解 決方法,方程式(2 )In 1984, KRIEGER. Publ., MALABAR " Natural frequency and mode shape A formula 11 and other vacuum internal resonance wall characteristic functions (3, 4), etc., were derived from the speed and pressure of all systems. For example, the velocity at any point on the wall can be opened from equation (1) st. c〇 / ⑽) = Σ Ypiij ^) 'F〇i (it〇) * ^ pi (x〇.y〇)' ^ pi (xy) (1) When coupled to the motor lumped element network and its immediate In the case of acoustic boundary, this series represents a solution to the differential equations that explain the screen polar wave. Equation (2)
第13頁 4 62 20 1 五、發明說明(ίο) 特性。0 p;的正交特性就是對微分方程式(2 )具有適當解決 方法的一項必需條件。自方程式(2)的均質形式求出該組 特性函數及其參數,亦即,在關掉此等驅動力以後。在此 |案例中,諧振壁只能以其自然頻率或所謂特性頻率(;) ;震動,以求滿足邊界條件。.. 在方程式(2)中,0pi(x,y)犹是在那裡觀察此種速率時的 位置處之第i項屏極特性函數的數值。0pi(XQ.yc))則為在那裡 I將驅動力Fpi(jt0)加至諧振壁時的位置處之特性函數。該項 :驅動力並包含有關在(X。,y。)時之驅動調速控制器之機電組 丨件的轉移功能,舉例說吧,諸如激發器,懸吊等。由於此Page 13 4 62 20 1 V. Description of the Invention (ίο) Features. The orthogonality of 0 p; is a necessary condition for a proper solution to the differential equation (2). The set of characteristic functions and their parameters are obtained from the homogeneous form of equation (2), that is, after turning off these driving forces. In this case, the resonant wall can only vibrate at its natural frequency or the so-called characteristic frequency (;); in order to satisfy the boundary conditions. .. In equation (2), 0pi (x, y) is still the value of the i-th screen characteristic function at the position where such a rate is observed. 0pi (XQ.yc)) is the characteristic function at the position where I adds the driving force Fpi (jt0) to the resonance wall. This item: The driving force includes the transfer function of the electromechanical group of the drive speed controller at (X., y.), For example, such as an exciter, suspension, etc. Thanks to this
I :種驅動力視驅動點處之諧振壁速率而定,故具有諸如關於 :機械音響耦合的類似反饋狀況為在於驅動點處,雖然,這 種效應實際上非常微小。I: The driving force depends on the resonance wall speed at the driving point, so similar feedback conditions such as about: mechanical acoustic coupling are at the driving point, although this effect is actually very small.
I 圖1 0提供分佈模揚聲器壁上面之一單獨特性函數之速率 大小分佈的實例。該等黑線均為其間速率為零時的波節 線。於增加模式指數時,則速率圖案會成為更加複雜。就 中度尺寸的諧振壁言,必定會總和大約2 0 0個模,以期涵 蓋音頻範圍。 模式導納〔YpKj ω〕為此等模式之權衡函數並且隨著那 一種幅度而決定以及在那一種相位時,第i模式才會加入 !方程式(1 )的總和中。根據方程式(3 )的說明,Ypi視驅動頻 率,屏極特性值,以及,在本文件之本文中最重要的,視 封閉體之音響阻抗以及因自由電磁場輻射而起之阻抗而 定。I Figure 10 provides an example of the magnitude distribution of a single characteristic function above the wall of a distributed mode speaker. These black lines are nodal lines at which the velocity is zero. As the mode index is increased, the rate pattern becomes more complicated. As for the medium-sized resonance mural, it is bound to add up to about 200 modes in order to cover the audio range. The mode admittance [YpKj ω] is a trade-off function of these modes and is determined by which amplitude and at which phase, the i-th mode is added to the sum of! Equation (1). According to the equation (3), Ypi depends on the driving frequency, the characteristics of the screen, and, most importantly, in this document, depending on the acoustic impedance of the enclosure and the impedance due to free electromagnetic field radiation.
第14頁 462201 五、發明說明(11) Y,Page 14 462201 V. Description of the invention (11) Y,
Sn * dr pi(s) ?pi Sp + Sp-dpi + γ^ι (3) 31) = 3/%為對基本諧振壁頻率(0[))所正常化的1^?13〇6頻 率變數(ωρ),此變數則視諧振壁之彎曲硬度!^及質量Mp而 定,亦即ωρ2 = Κρ/Μρ。Rpi為因材料損失而起之模式電阻並係 Sp= λρί時之諧振來說明Ypi(jw)的數值。Api為一定比因素並 為第i屏極特性值λ pi以及總輻射阻抗Zmai的函數,和方程 式(4)中所說明的一樣。Sn * dr pi (s)? Pi Sp + Sp-dpi + γ ^ ι (3) 31) = 3 /% is a 1 ^? 13〇6 frequency variable normalized to the fundamental resonance wall frequency (0 ()) (Ωρ), this variable depends on the bending stiffness of the resonance wall! ^ And the mass Mp, that is ωρ2 = κρ / Μρ. Rpi is the mode resistance due to material loss and is the resonance at Sp = λρί to explain the value of Ypi (jw). Api is a function of a certain ratio and is the function of the i-th screen pole characteristic value λ pi and the total radiation impedance Zmai, as described in equation (4).
Tpi(s) = . λρί +sp-Zmai(j〇>) 、p · iVlp 在真空情形(2mai = 0 )時,方程式(3 )中之第二項隨著減幅 因素dpi變為二次通頻帶轉移函數。圖1 1表示當在邊緣處被 夾住時之一諧振壁之首先1 0個模式的真空内Ypi(jft〇之頻率 響應規模。諧振壁特性頻率均與此等曲線的尖峯吻合。 如果現在將同一諧振壁安裝在一封閉體上,不僅按頻率 轉移此等模式,而且也根據圖1 2所見的予以修正。此舉之 發生乃係由於諧振壁與封閉體的兩種模式系統之間的互動 結果,此處全系統的模式導納就不再像真空内案例中一樣 為一種二次函數。事實上,可以一種高次多項式來擴大方 程式(3 )的分母,此舉將會顯示其合成擴大的特性函數。 圖1 3之頻率響應圖表乃係表示封閉體對諧振壁速率頻譜 的效應。在相同驅動條件下來計算兩條頻率響應曲線,不Tpi (s) =. Λρί + sp-Zmai (j〇 >), p · iVlp In a vacuum situation (2mai = 0), the second term in equation (3) becomes quadratic with the reduction factor dpi Passband transfer function. Figure 11 shows the frequency response scale of Ypi (jft0) in the vacuum of the first 10 modes of one resonance wall when clamped at the edge. The characteristic frequencies of the resonance wall all coincide with the peaks of these curves. If now Mounting the same resonant wall on a closed body not only shifts these modes by frequency, but also corrects them as seen in Figure 12. This occurs because the two modes of the system between the resonant wall and the closed body occur. As a result of the interaction, the model admittance of the whole system is no longer a quadratic function like in the vacuum case. In fact, a higher-order polynomial can be used to expand the denominator of equation (3), which will show its composition. Enlarged characteristic function. The frequency response chart in Figure 13 shows the effect of the closed body on the resonance wall velocity spectrum. Two frequency response curves are calculated under the same driving conditions.
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第15頁 4 6 2 2 0 1 五、發明說明(12) 過,左方曲線顯示真空内案例,而右方曲線則表示將此諧 振壁之兩個側面都裝載有一封閉體時的速率。曾將一雙封 閉體使用在此實例中,以求排除空氣的輻射阻抗。觀測點 乃係在激發器之驅動點處。清晰可見的為此種諧振壁特性 頻率轉移對也在圖1 2中所見的右圖中之較高頻率的影響。 值得一提的是,由於封閉體.影響以及模式數目和密度上的 後來增加結果,才會獲得說明速率頻譜的一條更均勻分佈 曲線。 其機械輻射阻抗則為因輻射而起之電抗作用力與諧振壁 速率的比值。就一單獨模式言,可將此種輻射阻抗(視為 諧振壁面積上面的常數並可以一種單獨模式之音響輻射功 率Pai的字眼表示之。這樣,才可由方程式(5 )來說明第i模 式之模式輻射阻抗。 z 2Page 15 4 6 2 2 0 1 V. Explanation of the invention (12) However, the left curve shows the case in a vacuum, and the right curve shows the rate when a closed body is loaded on both sides of the resonance wall. A pair of closures was used in this example to exclude the radiation impedance of air. The observation point is at the driving point of the exciter. What is clearly visible is the effect of this resonance wall frequency shift on the higher frequencies that are also seen in the right graph in Figure 12. It is worth mentioning that a more uniform distribution curve describing the rate spectrum will be obtained due to the effects of the closed volume, and the subsequent increase in the number and density of modes. Its mechanical radiation impedance is the ratio of the reactive force due to radiation to the velocity of the resonant wall. For a single mode, this radiation impedance (considered as a constant above the area of the resonance wall and can be expressed in terms of the acoustic radiation power Pai of a single mode. In this way, the i-th mode can be described by equation (5) Mode radiation impedance. Z 2
Zma i - 2 Jr < V] > (5) < Vi >為關於第i模式之諧振壁上面的平均速率。由於將 此數值施以平方,所以永遠為正值及實數,故輻射阻抗 zmai的特性均與音響功率之特性發生直接關連,此種阻抗 一般而言均為一複數值。Pai之實值部分等於輻射遠場功 率,此功率對zmai之電阻性部分具有貢獻,以造成諧振壁 之速率場的減輻。Pai的想像部分係由耦合系統之能量儲存 機構所造成,以便對z„ai之電抗正值或負值讓步。 一項正值電抗係由音響質量的出現所造成。舉例說吧,Zma i-2 Jr < V] > (5) < Vi > is the average velocity above the resonance wall of the i-th mode. Since this value is squared, it is always a positive value and a real number. Therefore, the characteristics of the radiation impedance zmai are directly related to the characteristics of the acoustic power. Such impedances are generally complex values. The real value of Pai is equal to the radiated far-field power. This power contributes to the resistive part of zmai, which results in a reduction of the rate field of the resonant wall. Pai's imaginary part is caused by the energy storage mechanism of the coupling system in order to concede the positive or negative reactance of z „ai. A positive reactance is caused by the appearance of sound quality. For example,
第16頁 此 電 理 動 簧 462201 五、發明說明(13) 乃輻射在自由空間内之實例。在另一方面,z 抗可表不具有等量硬度之一密封封閉體的存在 犖名稱’一項"質量"式輻射阻抗係由沒有壓縮 所造成’而當壓縮空氣且並未轉移它時,則有 n式阻抗存在。 輻射阻抗之想像部分的主要效應為諧振壁之真 頻率的轉移。一項Zmai的正值電抗(質量)會造成屑 頻率之下移’而—項負值電抗(硬度)則將特性頻 在已灰頻率抑’窗玻璃模式(pane mode)本身| 一種效應將$掂± ^ 7 主旱握主控杻。此種現象係由圖1 4之圖 ,彈V:】解ΐ示對稱的模式形狀會造成空氣的壓 移,以i Π: ϊ 對稱的模式形狀則使空氣 則並未在任一=響的”質量"行為表現。當它們 體電抗之互動=ί統中出現的新模式均係由諧振 反動所產生的。 圖1 5表示此種球 線。左方圖表顯/閉肢輻射阻抗之想像部分的頻 "彈簧式1'電2二=由=對稱窗玻璃模式所典型地 部分均為負i1向,第一封閉體特性頻率時,此 内特性頻率。在並係上移均在此頻區以内之諧振 玻璃模式所典细t比時,右方圖表則顯出由一種 如果封閉體是密2的"質量式二電抗行為表現 部,和這裡我’,且具有與窗玻璃表面平行 轄射阻抗為方程H)例—樣,那麼,第i屏極模 之負值 。依據物 的空氣運 一項”彈 空内特性 極特性 率上移。 1指揮那 解來澄 縮,即 作左右轉 分開時, 壁與封閉 率響應曲 產生的 種電抗大 璧的真空 #對稱窗 〇 之剛性壁 尤的機械 462201 五、發明說明(14) Zjnai = 一 .ω·ρ3 Σ (6} W(i.k,u為考慮橫斷面邊界條件並涉及屏極和封閉體特性 函數的耦合積分。方程式(6)中的指數i為屏極模數目;Lri 為封閉體的深度;以及kz為z方向(與窗玻璃垂直)内之模 式波數目成分。就一具剛性矩形封閉體言,kz係由方程式 (7 )說明的: kz{k.l)=Page 16 This electromechanical spring 462201 V. Description of invention (13) is an example of radiation in free space. On the other hand, the z-resistance indicates the existence of a sealed enclosure with the same amount of hardness. The name 'item " quality " radiation resistance is caused by no compression' and when compressed air does not transfer it When there is n-type impedance. The main effect of the imaginary part of the radiation impedance is the transfer of the true frequency of the resonance wall. A positive Zmai reactance (mass) will cause the chip frequency to shift down ', while a negative reactance (hardness) will reduce the characteristic frequency to the gray frequency and suppress the pane mode itself | an effect will $掂 ± ^ 7 The main drought grips the main control 杻. This phenomenon is shown in the graphs in Fig. 1 and 4. V:] solution shows that the symmetrical pattern shape will cause the pressure of the air, and the symmetrical pattern shape of i Π: ϊ makes the air not at any level. Quality " Behavioral performance. When the interaction of their body reactance = the new modes appearing in the system are all caused by resonance reaction. Figure 15 shows such a spherical line. The left diagram shows the imaginary part of the radiated impedance of the limb. The frequency of the spring-type 1'electricity 2 ==== symmetrical window glass mode is typically a negative i1 direction, the characteristic frequency of the first closed body, the characteristic frequency within this range. The parallel shift is at this frequency. When the ratio of fine t is typical of the resonance glass mode within the region, the right chart shows a "mass-type secondary reactance behavior part if the closed body is dense, and here I ', and it is parallel to the surface of the window glass The emission impedance is an example of the equation (H). Then, the negative value of the polar mode of the i-th screen. According to the air transport of the item, the "characteristic characteristics of the air inside the bomb moves up." 1 Command the solution to be condensed, that is, when the left and right turns are separated, the wall and the closing rate response curve generate a vacuum of large reactance #symmetric window 0. The rigid wall of the mechanical 462201 V. Description of the invention (14) Zjnai = 1.ω · Ρ3 Σ (6) W (ik, u is the coupling integral that considers the boundary conditions of the cross section and involves the characteristics of the screen and the closed body. The index i in equation (6) is the number of screen modes; Lri is the closed body. Depth; and kz is the component of the number of mode waves in the z direction (perpendicular to the window glass). For a rigid rectangular closed body, kz is described by equation (7): kz {kl) =
| 指數k及1均為X和y方向内之封閉禮正交模數目,此處Ldx I及Ldy均為此平面内之封閉體尺寸。Ao為窗玻璃的面積及Ad 為X及y平面内之封閉體的橫斷面積。 方程式(6 )為一種複雜函數,該函數詳細說明窗玻璃模 與封閉體模之互動。為求了解此項公式的性質計,讓我們 將它予以簡化,其法為只將此系統限制於窗玻璃之第一模 式及封閉體之Z模而已(k = 1二0 ) β此舉將會產生下刊簡化關 係。 ^maO = -j' Cot {kz · Ldz) 丨 Ad ,( ⑻ 方程式(8 )為一條封閉管之熟悉驅動點—阻抗,〔即方程 46-201 五、發明說明(15) 才可完成進一步簡化如 I式(6)〕。如若其乘積K: j 下 0The indices k and 1 are the number of closed ceremonial orthogonal modules in the X and y directions, where Ldx I and Ldy are the dimensions of the closed body in this plane. Ao is the area of the window glass and Ad is the cross-sectional area of the closed body in the X and y planes. Equation (6) is a complex function that specifies the interaction between the window pane and the closed phantom. In order to understand the nature of this formula, let's simplify it. The method is to limit this system to only the first mode of the window glass and the Z mode of the closed body (k = 120). This move will A simplified relationship will be generated. ^ maO = -j 'Cot {kz · Ldz) 丨 Ad, (⑻ Equation (8) is a familiar driving point-impedance of a closed tube, [ie equation 46-201 V. invention description (15) can be further simplified Such as I formula (6)]. If its product K: j under 0
ZZ
maO A; 1 (9) 式中,c ab /(p: )為容積vh之封閉體的音響依從。方 程式(9 )為封閉物之低頻集總元件模式。如果其來源為質 量Mms的剛性活塞並係以懸吊具有依從Cms,那麼,其基本” 模式"具有特性值λ pc>= 1以及方程式(4 )之耦合系統的定比 因素才會成為根據方程式(1 0 ),( 1 )所表示的熟悉關係, 並具有封閉體空氣容積Cmb = Cab/A()2的等值機械依從。 ϊρο 1 +maO A; 1 (9) where c ab / (p:) is the acoustic compliance of a closed body with volume vh. Equation (9) is the low-frequency lumped component mode of the enclosure. If the source is a rigid piston with mass Mms and the suspension has compliance Cms, then the basic "mode" of the coupling system with characteristic value λ pc > = 1 and equation (4) will become the basis. The familiar relationship represented by the equations (1 0) and (1), and has the equivalent mechanical compliance of the enclosed air volume Cmb = Cab / A () 2. Ϊρο 1 +
Cr (10) 已完成各種測試,以調 聲器的效應。除了在封閉 表現外,並曾設計各項實 測一分佈模揚聲器諧振壁 表現時,確立此類模式均 曾選擇不同尺寸及大部 壁作為我們的測試目標。 應為充分的不同尺寸及另 用的差別,以便按比例涵 查一淺薄背部封閉體對分佈模揚 體中一般查出DNM諧振壁的行為 驗來證明該項理論模式以及在預 與其封閉體之耦合模系統的行為 為精確所達到的限度。 分特性的兩個分佈模揚聲器諧振 所已決定的是,這些項目一方面 一方面在其大部分特性中都是有 蓋一種良好範圍。曾將第一組Cr (10) has completed various tests to determine the effect of the tuner. In addition to the closed performance, and have designed various measurements of the performance of a distributed mode speaker resonance wall, the establishment of such models have chosen different sizes and large walls as our test targets. It should be sufficient for different sizes and other differences in order to investigate the behavior of the DNM resonance wall in a shallow back enclosure versus a distributed mold lifter in proportion to prove the theoretical model and the effect of pre-existing enclosures. The limits of the behavior of a coupled-mode system for accuracy. Two distributed-mode loudspeaker resonances with different characteristics It has been decided that these projects, on the one hand, have a good range in most of their characteristics. The first group
第19頁 4 6 2 2 0 1 五、發明說明(16) "A"選擇為具有三種不同大部分機械特性之U9厘来χ21〇 厘米之細小Α5尺寸諸振壁。具有聚碳酸酯蜂窩上之Α5_ 1聚 碳酸S旨膜;Rohacel 1上之Α5-2碳纖維;以及設有皮膚的 A5-3 Rohacell。曾經選擇’’B"組為更大的8件,大約達42〇 厘米X 5 9 2厘米的A2尺寸。並.曾.以聚碳賴蜂窩°核上的.玻璃 纖維膜製造A 2-1 ,而A2-2則為鋁質蜂窩上的碳纖維膜。表 i列舉這些東西的大部分特性。1由 激發器 在最佳情況點處完成調速控制作用。曾採用兩種型式的激 發器’在這裡它所曾最適合測試下⑼振壁尺寸。在則 振壁案例中,曾以Bl = 2. 3 丁m ,Re = 3. 7 在以Β1=1· 0 Tm,Re = 7. 3 Ω 及Le = 36 以 η 6" ^ 例中則採用-種U厘純式。小Page 19 4 6 2 2 0 1 V. Description of the invention (16) " A " The small A5 size vibrating walls with U9 centimeters and χ2120 centimeters with three different most mechanical characteristics are selected. A5_1 polycarbonate S film on polycarbonate honeycomb; A5-2 carbon fiber on Rohacel 1; and A5-3 Rohacell with skin. The '' B " group was once chosen to be a larger 8 pieces, approximately A2 size of about 42 cm x 592 cm. In addition, A 2-1 was made of glass fiber membranes on polycarbonate honeycomb cores, while A2-2 was a carbon fiber membrane on aluminum honeycombs. Table i lists most of these characteristics. 1 The speed control function is performed by the exciter at the best case point. Two types of exciters have been used. Here, it has been most suitable for testing the size of the vibrating wall. In the case of vibration walls, Bl = 2. 3 ding m and Re = 3. 7 were used in the case of B1 = 1.0 Tm, Re = 7. 3 Ω and Le = 36 in the case of η 6 " ^ -U type pure type. small
Zm 尺寸 _(Ns/m) (mm) 一 24.3 5X592X420 ^ 60.0 7.2X592X420 _ 7.5 2X210X 149 _1Ι·8 2X210X149 2.7 3X210X149 曾利用懸吊及音響密封用之 諧振壁安裝在具有可調整深度 28,40上將封閉體深度製造為 mm以及在20,50,95上製造1 測量均係就每項測試案例以不 木軟聚氦基曱酸乙酯泡沫將 的背部封閉體上。曾於1 6, 可調整與"A11組諧振壁的5 3 組错振壁的130 mm。各種 @ #閉體深度予以完成並將Zm size _ (Ns / m) (mm)-24.3 5X592X420 ^ 60.0 7.2X592X420 _ 7.5 2X210X 149 _1 1 · 8 2X210X149 2.7 3X210X149 The resonance wall used for suspension and sound sealing was installed on the adjustable depth 28, 40 The closures were manufactured in mm depth and manufactured at 20, 50, 95. 1 Measurements were made on the back closures with a non-wood soft polyhelium ethyl acetate foam for each test case. It has been adjusted from 130 to 130 mm with 5 and 3 sets of stray walls of the "A11" resonance wall. Various @ #closed body depth to complete and
諧振壁 型式 B (Nm) Α2-1 PC核上有玻璃 10.4 Α2-2 A1核上有碳 57.6 Α5^1 PC核上有PC 1.39 Α5-2___. Rohacell上有破 3.33 Α5-3 Rohacell 核心 0.33 第20頁 4 6 2 20 1 五、發明說明(17) 結果製成文件 曾利用雷射震動計測量错振壁速率及位移。並係用16〇〇 點的線性頻率音階涵盖重要頻率範圍。曾採用圖16中所表 示的裝置來測量错振壁機械阻抗,其方法為計算驅動點處 所施加的作用力與諧振壁速率的比值。 Ζ. Τ 依此種程序,自激發器的集總參數資訊計算所施加的作 同力。雖然其本身的諧振壁速率反饋在電機電路内’但直 耗合則十分微弱。式中所能表示的,為就激發gB1之微 小數值(1至3 Tm )言,假定㈣放A器輸出阻抗微小(常數 電壓Η反饋至此種電㈣統的模式轉合就會充分微弱 :難以使此種假定令人雀躍。所以,彳會將來自此種近似 =微小誤差略而不計。圖18ay表示错振壁 :機械阻抗…員資料均係得自由雷射震動計所測量之諸 及施加作用力的測量值。注意,每項封閉體深度 的阻抗最小值均係發生在系統諧振模式處。 J種諧振壁之聲壓水平及極性響應;句:在3 5 〇立方公尺 ^大空間内所測得的並係利用視測量而定之MLSSA就消 H 1 2至1 4 MS予以閘控的。根據圖丨7d中的表示及圖 =所示之裝置利用-種9微音陣列系統完成功率測量。就 各種封閉體深度將此等測量數繪製在圖l9a至f中。由圖表 上的標記來凸顯系統證振。Resonant wall type B (Nm) Α2-1 PC with glass 10.4 Α2-2 A1 with carbon 57.6 Α5 ^ 1 PC with PC 1.39 Α5-2 ___. Rohacell with 3.33 Α5-3 Rohacell core 0.33 No. 20 pages 4 6 2 20 1 V. Description of the invention (17) The results were documented. The laser vibrometer was used to measure the velocity and displacement of the staggered wall. The linear frequency scale of 160 points is used to cover the important frequency range. The device shown in Figure 16 was used to measure the mechanical impedance of the staggered wall by calculating the ratio of the applied force at the driving point to the velocity of the resonant wall. TZ. According to this procedure, the lumped parameter information of the self-exciter calculates the same force applied. Although its own resonant wall rate feedback is within the motor circuit ', the direct loss is very weak. What can be expressed in the formula is to excite the small value of gB1 (1 to 3 Tm), assuming that the output impedance of the amplifier A is small (constant voltage, the mode transition fed back to this electrical system will be sufficiently weak: difficult Makes this assumption exciting. Therefore, I will ignore this approximation = small error. Figure 18ay shows the wrong vibration wall: mechanical impedance ... The data of the member are all measured and applied by the free laser vibrometer. The measured value of the acting force. Note that the minimum impedance value of each closed body depth occurs at the resonance mode of the system. Sound pressure levels and polar responses of the J-type resonance walls; Sentence: in a large space of 3 500 cubic meters Measured in the inside and gated by HLS 2 to 1 4 MS using MLSSA depending on the measurement. According to the representation in Figure 丨 7d and Figure = The device shown is completed using a 9-microphone array system Power measurement. These measurements are plotted in Figures 19a to f for various closed-body depths. The system's vibration is highlighted by the marks on the chart.
第21頁 462201 五、發明說明(18) 就一個28厘米深度封閉體來測量該等A5-1及A5-2諧振壁 之極丨生響應並將其結果表示在圖及2〇b中。當與圖1中 之自由分佈模揚聲器的極性響應比較時,它們證明了封閉 背部分佈模揚聲器在其改良方向性方面的意義β 為進一步調查封閉體對諧振臂行為表現的影響計,特別 是在組合系統諧振時,曾完成一項特別耦合,以容許在9 個預定點處測量封閉内的内部壓力,和圖21中所表示的一 樣。將微音器插在以一項預定深度所設在一 A 5封閉體耦合 之背部屏極内部的洞口中,同時用硬橡膠索環緊密地堵塞 其他8個位置洞口《在測量期間内’則由一適當橡膠索環 將微音器與封閉體施以機械隔離。 從此種資料曾產生一輪廟圖形’以表示系統t皆振時之壓 力分佈以及在此頻率之任意一邊均和圖22a至c中所表示的 情形一樣。就圖27中所表示之9個位置亦繪製壓力頻率響 應曲線。此種曲線圖乃係就有關封閉體内之測量點的全部 曲線展現諧振區内之良好清晰度。但是’其壓力卻係隨著 增加頻率在封閉體橫斷面面積上具有改變的傾向。 以掃描雷射震動計測量此等諧振壁上面的速率及位移之 垂直成分》並繪製此等諧振壁上面之速率及位移分佈曲 線,以調查此種耦合系統諧振壁周圍之諧振壁的行為表 現。將其結果製成文件龙將若干案例表示在圖24a至d中。 此等結果乃係以諧振壁移動的全部建議該譜振壁在諧振時 之定普鼓模式行為表現,雖然當我們移向错振壁邊緣時, 都是用較小的速率和位移°Page 21 462201 V. Description of the invention (18) The polarized responses of the A5-1 and A5-2 resonant walls are measured on a 28 cm deep closed body and the results are shown in the figure and 20b. When compared with the polar response of the free-mode speaker in Figure 1, they demonstrate the significance of the closed-back distributed-mode speaker in terms of its improved directivity. Β To further investigate the effect of the closed body on the behavior of the resonant arm, in particular When the combined system resonated, a special coupling was completed to allow the internal pressure inside the enclosure to be measured at nine predetermined points, as shown in Figure 21. Insert the microphone into the opening inside the back panel coupled to an A5 enclosure at a predetermined depth, while tightly blocking the holes in the other 8 positions with a hard rubber grommet. The microphone is mechanically isolated from the enclosure by a suitable rubber grommet. From this kind of data, a round temple pattern 'has been generated to indicate the pressure distribution when the system t is vibrating and on either side of this frequency, as is the case shown in Figs. 22a to c. Pressure-frequency response curves are also plotted for the nine positions shown in FIG. This kind of graph shows the good definition of the resonance region for all the curves about the measurement points in the closed body. However, its pressure tends to change in the cross-sectional area of the closed body with increasing frequency. Measure the vertical components of the velocity and displacement above these resonance walls with a scanning laser vibrometer and plot the velocity and displacement distribution curves above these resonance walls to investigate the behavior of the resonance walls around the resonance walls of this coupling system. The results are documented. Several cases are shown in Figures 24a to d. These results are based on all the suggestions of moving the resonant wall. The performance of the fixed drum mode of the spectral wall at resonance is suggested, although when we move to the edge of the staggered wall, we use a smaller rate and displacement °.
4 6 2 20 14 6 2 20 1
五、發明說明(19) 實際上’此種行為表現就諧振壁之全部條件言均属 致’雖然模式形狀均會逐例改變’但卻視一纟且複雜參數 定,包括諧振壁硬度,質量,尺寸以及邊界條件萁。 而 、 τ。依其 限度及就一無限剛性諧振壁言,當活塞之基本剛性本體模 式作用於諧振壁空氣容積的剛性時,才會看到此種系統^ 振的情況。曾發現將此種分佈模揚聲器系統諧振稱為,,全^ 部本體模式”或WBM頗為便利。 已由新轉換器有限公司在一套軟體中實施了此種耦合系 統之全部理論導出。此項計劃之一種型式曾被用來模擬本 文中我們測試目標的機械音響行為表現。此種包裹確能考 慮關於一諧振壁’激發器及有關一框架或一封閉體的機械 丨音響介面之全部電氣,機械和音響變數以及在其他參數中 |間預測遠場聲音響壓力,功率和全系統之方向性。 圖2 5 a表示被夾住在一框架内用以自兩侧等量韓射在— f由空間中之A 5 -1諧振壁的一種自由輻射之對數速率頻 1 °貫線代表模擬曲線以及虛線為測量速率頻譜。在低頻 卞,遠諧振壁隨著激發器進入諧振。1 〇 〇 0赫以上之頻率範 圍中的缺點係因模擬模式内缺乏自由場輻射阻抗所致。 | 圖2 5 b表示和圖2 5 &中一樣的相同諧振壁,但此時卻加栽 |有兩個相同封閉體,馆振壁之每一側面上均有_個封閉 丨收’其橫斷面和諧振壁相同並有2 4厘米的深度。設計並採 |用—種雙封閉體,以期排除諧振壁之一個側面上的自由電 丨磁场的輪射阻抗並使實驗成為與此種自由場輪射阻抗無 I關°要注意這一點頗為重要,那就是只將此種實驗室設備V. Description of the invention (19) In fact, 'this behavior is based on all the conditions of the resonance wall', although the shape of the mode will change from case to case, but it depends on complex parameters including the hardness and quality of the resonance wall. , Size and boundary conditions 萁. And, τ. According to its limits and on an infinitely rigid resonant wall, the vibration of such a system will only be seen when the basic rigid body mode of the piston acts on the rigidity of the air volume of the resonant wall. It has been found that it is convenient to call this distributed mode speaker system resonance, "full body mode" or WBM. The entire theory of this coupling system has been implemented by a new converter company in a set of software. This A type of project has been used to simulate the mechanical and acoustic behavior of our test target in this article. This package does take into account all the electrical aspects of a resonant wall 'exciter and a mechanical or acoustical interface of a frame. , Mechanical and acoustic variables, and among other parameters, the far-field sound pressure, power, and directivity of the whole system are predicted. Figure 2 5a shows that it is clamped in a frame for equal amount of Korean shots from both sides— f is a logarithmic rate of free radiation of the A 5 -1 resonant wall in space. The 1 ° through line represents the analog curve and the dotted line is the measurement rate spectrum. At low frequencies, the far resonant wall enters resonance with the exciter. 1 〇〇 The disadvantage in the frequency range above 0 Hz is due to the lack of free-field radiation impedance in the analog mode. | Figure 2 5b shows the same resonance wall as in Figure 2 5 & Plant | There are two identical enclosures, each side of the museum's vibrating wall has _closes 丨 closes '', its cross section is the same as the resonant wall and has a depth of 24 cm. Design and use Body, in order to exclude the free-radiation magnetic field on one side of the resonance wall, and make the experiment independent of this free-field free-radiation impedance. It is important to note that this is the only type of experiment Room equipment
第23頁 462201 ' 五、發明說明(20) ^ 使用於理論證實而已。 為期促成此種諧振壁的速率測量計,曾以一種透明材料 製造兩個封閉體之後壁,以容許雷射光束按達諧振壁表^ |面。曾利用t皆振壁A 5 - 3使有皮膚但不同大部分特性的 Rohacell重覆此種試驗並將某转果表示在圖26a及b中。在 兩個案例中,均使用2 0 0點的對數範圍完成模擬,而雷射 測量則使用1 6 0 0點的線性範圍。 自前述理論及工作看來,顯然,適合分佈模揚聲器的細 小封閉體隨著它在若干好處中間帶有一項奇異缺點。由於 根據圖27a及b中所表示之系統諧振時之WBM的緣故,此舉 顯示過大的功率。值得一提的是,除了此項尖峯外,在全 部其他特色中,此種封閉式分佈模揚聲器均能貢獻一項真 正改良的性能,包括全部增加功率頻帶寬在内。 所已發現的是,在大多數案例中,均可設計一種適當Q 值的簡單二次帶停等化網路。以等化此種響應尖峯,該項 Q值則係匹配該項功率響應尖峯的Q值。而篡’在有些案例 中,一具單極高通濾波器常常會調節此種情況,其方法為 傾斜低頻區,以提供一項寬廣平坦的功率響應。由於分佈 模揚聲器諧振壁之獨特性質及其電阻性電氣阻抗響應的緣 故,無論濾波器為主動或被動,其設計仍將維持非常簡單 樸素。圖28a表示在其中加入一帶停被動濾波器供等化用 的位置。也可在在圖2 8b及c中見到另外實例’該圖表示單 極EQ作為與揚聲器成串聯的所使用之一電容器β 我們已在本文中表示,當使用的分佈模揚聲器接迎並平Page 23 462201 'V. Description of the Invention (20) ^ It is only used for theoretical verification. In order to promote such a resonance wall rate meter, the rear wall of two closed bodies was made of a transparent material to allow the laser beam to reach the surface of the resonance wall. Rohacell, which has skin but different most of its characteristics, has been used to repeat this kind of test with t all vibration walls A 5-3 and a certain result is shown in Figs. 26a and b. In both cases, simulations were performed using a logarithmic range of 200 points, while laser measurements used a linear range of 160 points. From the foregoing theory and work, it is clear that a small enclosure suitable for distributed mode speakers comes with a strange disadvantage among several benefits. This shows excessive power due to the WBM when the system is resonant as shown in Figures 27a and b. It is worth mentioning that in addition to this spike, among all other features, this closed distributed mode speaker can contribute a truly improved performance, including all increased power frequency bandwidth. What has been found is that in most cases, a simple quadratic stop-and-equalization network with an appropriate Q value can be designed. To equalize such a response spike, the Q value matches the Q value of the power response spike. In some cases, a single-pole high-pass filter often adjusts this situation by tilting the low-frequency region to provide a broad and flat power response. Due to the unique nature of the resonant wall of the distributed mode speaker and its resistive electrical impedance response, the design will remain very simple and simple, regardless of whether the filter is active or passive. Fig. 28a shows a position where a passive filter with a stop is added for equalization. Another example can also be seen in Figure 2 8b and c. The figure shows the unipolar EQ as one of the capacitors used in series with the speaker β. We have shown in this article that when the distributed mode speaker is used,
第24頁 462201 五、發明說明(21) 行於壁部時,必須特 極特性而起之最小互 數,所以,無法予以 射面,在延伸此種系 是,此舉卻可能並非 所亦在圖中表示的 |封閉體將會使它成為 !音響性能上成為可以 ;一種分佈模揚聲器用 j產生了分佈模揚聲器 ]之間的一項尖銳對比 然可由比較簡單的計 !内錐形體之機械音響 II I封閉體之機械音響特 j關係在設有適當工具 I 所觀察到的是,系 丨化β在將其深度與諧 ;都非常顯著。可是, '時,低頻響應中的增 :一封閉體内之剛性活 特複雜雙 離之函 之完整反 優點,可 器的極小 系統在其 證明了將 。此舉卻 輻射體者 的是雖 現一種箱 聲器及其 係,此種 能預測。 時的變 情形中, 度以外 ,這是與 別小心來確保與後者因其獨 動。此種互動為距邊界的距 普偏性地固定起來》諧振壁 統之低頻響應時,具有肯定 許多應用上的實用提議。 是,使用於一種分佈模揚聲 與其立即環境無關並使此種 預測。所開發的數學模式則 在耦合系統中的複雜性程度 之預測及設計與傳統式活塞 。自此項工作看來非常清晰 算(甚至由一手用計算機)發 特性,但有關一種分佈模揚 性卻係受制於複雜的互動關 時就會使此種系統成為不可 統性能隨著改變封閉體容積 振壁尺寸比較時微不足道的 也會看到的是,在某一種深 加就會成為邊緣性了。當然 塞相符一致的。舉例說吧,可設計一 種具有50厘米封閉體深度呈Α2尺寸諧振壁擁有向下伸至大 約1 2 0赫的頻帶寬,圖2 4。 看到一種具有細小封閉體之分佈模揚聲器的另一特色就 是此種系統之中間及高頻響應中的一項顯著改良。此種情Page 24 462201 V. Description of the invention (21) When traveling on the wall, the minimum mutual number due to extreme characteristics must be used, so it cannot be projected. In extending this system, this may not be the case. The enclosed body shown in the figure will make it become! Acoustic performance is possible; a sharp contrast between a distributed mode speaker and a distributed mode speaker is generated by a simpler calculation! The mechanical sound characteristics of the closed sound body of the sound II I are observed with the appropriate tool I. It is observed that the system β is in depth and harmonic; both are very significant. However, at the time, the increase in low-frequency response: a rigid activity in a closed body, the complete counter-advantage of the complex double-difference function, and Kee ’s minimal system proves that. What the radiator did was that although a speaker and its system were present, this was predictable. In time-changing situations, beyond the degree, it is important to be careful to ensure that the latter is independent because of it. This kind of interaction is fixed at a distance from the boundary. The low-frequency response of the resonant wall has practical proposals that affirm many applications. Yes, the use of a distributed mode speaker has nothing to do with its immediate environment and makes such predictions. The developed mathematical model predicts and designs the degree of complexity in coupled systems with traditional pistons. From this work, it seems very clear (even by first-hand computer) that the characteristics of a distributed model are subject to complex interactions, which will make such systems become unregulated. It is also insignificant when comparing the size of the volume vibration wall that it will become marginal at a certain depth. Of course, the plugs are consistent. For example, a resonant wall with a closed body depth of 50 cm and a size of A2 can be designed to have a frequency bandwidth extending down to about 120 Hz, as shown in Figure 24. Another feature of a distributed-mode speaker with a small enclosed body is a significant improvement in the middle and high frequency response of such a system. Such feeling
第25頁 4 6 2 20 1 :五、發明說明(22) ;況已出現在本文的許多測量及模擬曲線中,當然,也是該 !項理論所預期的。顯然,此種諧振壁系統模式性的增加乃 I係對此種改良擔負大部分的責任,不過,封閉體損失亦可 !能藉增加此種系統的全面減幅而影響此種情況。 ! 將含有此種諧振壁之背後輻射視為一種自然結局時,則 :此種封閉系統之方向性實質上會自一種雙極形狀改變為圖 1 7中所振示的近乎心形行為表現的態勢。所預期的是,有 '關一種封閉背部的分佈模揚聲器的方向性可能會在某些應 ;用上找到用途,那裡較強的橫向涵蓋範圍卻是合意的。 ! 當與封閉式分佈模系統工作時,才發現功率響應測量數Page 25 4 6 2 20 1: V. Description of the invention (22); the situation has appeared in many of the measurement and simulation curves in this article, of course, it is also expected by this theory! Obviously, the modest increase of such a resonant wall system is that I is responsible for most of this improvement, but the loss of the closed body can also affect this situation by increasing the overall reduction of this system. When the radiation behind this resonant wall is regarded as a natural ending, then the directionality of this closed system will change from a bipolar shape to a nearly heart-shaped behavior shown in Figure 17 situation. It is expected that the directivity of a distributed-mode loudspeaker with a closed back may find use in some applications, where strong lateral coverage is desirable. ! Power Response Measurements Only Found When Working with a Closed Distributed Mode System
I !最為有用,以期觀察可能需要補償之過多能量區。此點均 !與對分佈模揚聲器所完成的其他工作一致,在其中所發現I! Is most useful in order to observe areas of excessive energy that may require compensation. This is consistent with other work done on distributed mode speakers, where it was found
I |的是,其功率響應則為正好係關於分佈模揚聲器之主觀性 |能的最富代表性音響測量。採用此種功率響應時,所曾發 ;現的是,實施的,一個簡單通頻帶或一單極高通濾波器才 :是將此區内之功率響應等化所必需的全部。 丨 值得一提的是,這裡所進行的各種試驗,在識別此種系 ;統之完整本體模式及其附帶特性時,均已表現了良好程度 I的相互關連。I | is that its power response is just the most representative acoustic measurement of the subjective nature of distributed mode speakers. When using this kind of power response, it has been found that what is implemented is a simple passband or a single-pole high-pass filter: all that is necessary to equalize the power response in this region.丨 It is worth mentioning that the various tests performed here have shown a good degree of interrelationship in identifying the complete ontology model of the system and its incidental characteristics.
第26頁 462201 案號1 88105770 (7 C年、7月台曰 修正 元件符號說明 五、發明說明(23) 1 密封箱揚聲器 2 箱形封閉物 3 後壁 4 震動激發器 5 諧振形音響輻射體 6 彈性懸吊 7 對立彈性條片 8 框架 9 > 1 0 框架構件 11 扣件 12 硬化筋條 13 空腔 14 内部表面Page 26 462201 Case No. 1 88105770 (Description of Correction Element Symbols in July, July C, July 5. Explanation of the Invention (23) 1 Sealed Box Speaker 2 Box Closure 3 Rear Wall 4 Vibration Exciter 5 Resonant Acoustic Radiator 6 Elastic suspension 7 Opposite elastic strips 8 Frame 9 > 1 0 Frame member 11 Fastener 12 Hardened ribs 13 Cavity 14 Internal surface
O:\57\57900.ptc 第26a頁 2001.07. 05. 027O: \ 57 \ 57900.ptc Page 26a 2001.07. 05. 027
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GBGB9807316.6A GB9807316D0 (en) | 1998-04-07 | 1998-04-07 | Loudspeaker |
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HUP0103916A2 (en) | 2002-03-28 |
GB9807316D0 (en) | 1998-06-03 |
HK1030327A1 (en) | 2001-04-27 |
NZ506732A (en) | 2002-11-26 |
ID27518A (en) | 2001-04-12 |
KR20010042491A (en) | 2001-05-25 |
EA200001038A1 (en) | 2001-04-23 |
ATE334567T1 (en) | 2006-08-15 |
CN100417304C (en) | 2008-09-03 |
SK14932000A3 (en) | 2001-05-10 |
AU3340099A (en) | 1999-10-25 |
PL343440A1 (en) | 2001-08-13 |
HUP0103916A3 (en) | 2002-12-28 |
DE69932507D1 (en) | 2006-09-07 |
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