TW561788B - Acoustic device - Google Patents

Abstract

Acoustic device (1) comprising a panel-form member (2) capable of supporting bending wave vibration and having a frequency distribution of resonant bending wave modes, the member (2) being of substantially triangular form with the parameters of the member (2) being selected so as to provide a desired frequency distribution of resonant modes, wherein the parameters are selected from the ratio of the effective lengths of two of the sides (12, 14) of said triangular form, the effective angle (10) between at least two of the sides of said triangular form and the curvature of at least one side.

Description

561788 V. Description of the Invention (彳) Technical Field-In particular, the speakers of the dispersed mode type (hereinafter referred to as "DM speakers" in the present invention) Background technology = as described in WO 97 / _2 (herein referred to as a reference) is a description A loudspeaker including a radiator can support curved waves ¥ ¥ W ^ ㈣ pull wave, receive a-converter mounted on the sound = to excite the bending wave in the sound light emitter to generate a sound output. The characteristics of this sound radiator are selected to disperse the resonant bending wave mode that is uniform in frequency on the real f. In other words, the characteristics or parameters of the sound radiator: such as size, thickness, shape and material, etc., can be selected from Smooths the peaks of the frequency response caused by the "x" or "Γ cluster" of the mode. Therefore, the obtained resonance bending wave mode distribution can make it have the smallest cluster and interval difference. In particular, this kind of The characteristics of the sound radiator can be selected to distribute the resonance back curve mode of lower frequency substantially uniformly. The number of the resonance curve mode is less at low frequencies than at high frequencies. Therefore, the distribution of the lower frequency resonance_curvature mode is particularly important if the speaker needs to have an output to extend into this region. The lower frequency resonance bending wave mode is preferably 10 or 20 of the sound radiator Lowest frequency resonance bending wave chess style. The resonance bending wave mode of each conceptual axis of the sound radiator can be configured to stagger in frequency. Each conceptual axis has an associated lowest fundamental frequency (conceptual frequency) and Higher modal modes at frequency. By staggering the modes about each axis, a substantially uniform distribution can be achieved. There will be two conceptual axes. -4- This paper size applies to China National Standard (CNS) A4. Specifications (210 X 297 mm) 561788 A7 B7 V. Description of the invention (2 'The axis can be a symmetrical axis. For example, for a rectangular sound radiator', the axis can be a short axis and a long axis, which Parallel to the short side and the long side of the sound radiation benefit, respectively. The converter position of such a speaker is basically selected to be substantially uniformly light to the resonant bending wave mode. In particular, the position of the converter It can be selected to be substantially uniformly coupled to the lower frequency resonance bending wave mode. In other words, the converter can be installed away from as many nodes (or dead points) of the lower frequency resonance mode as possible. Therefore, the converter The position may be a position where the number of the anti-vibration active resonance anti-nodes is relatively high, and conversely, the number of the resonance anti-nodes is relatively low.

W0 97/09842 indicates that the panel has the form of a regular polygon or a non-regular polygon. A similar configuration is disclosed in WO 00/28781, which shows a pyramid and tetrahedral remains. Eight, it at least partially covers an air volume, so the f-curvature is coupled to the volume to provide a coupled resonant mode. X An object of the present invention is to improve the sound performance of such a resonant mode bending wave speaker having a substantially triangular panel distribution. Disclosure of the Invention According to one aspect of the present invention, it provides—a sound device comprising—a panel-shaped member capable of supporting f-curve wave vibration, and a frequency distribution of a wave mode, the member being substantially a parameter of a triangular piece. The frequency distribution 〆 is selected to provide a desired resonance mode, where the effective length 两侧 of the two sides of the triangle, the effective angle 之间 between the at least two sides, and at least one parameter are selected. . I choose the curvature on the side of -5-561788 A7 _____B7 V. Description of the invention (3) &quot; '----- This parameter can be selected individually or in combination to provide the desired frequency distribution. For example, the ratio of the effective length i of the two sides of the triangle can be selected to produce the desired distribution. The effective angle between the at least two sides can then be changed to see if a further improvement in the frequency distribution can be achieved. In addition, the selection of the angle causes the side to change, or the curvature of the selection, and then the change of the angle, etc. The desired frequency distribution may be more uniform, in which a frequency distribution of a rectangular panel-shaped member having one side of the triangle and the other side having the same length is used, and its aspect ratio is 1.134. The aspect ratio 1; 134 is the "gold" aspect ratio, as disclosed in WO 97/09842. In other words, the parameter is selected such that the non-uniformity of the frequency distribution of the triangular panel form member can be reduced compared to the rectangular panel form member. / This parameter can be selected to minimize the non-uniformity of the frequency distribution. By minimizing the non-uniform sentence, it can achieve a distribution with a substantially uniform frequency distribution of resonant bending wave modes. As understood from the aforementioned WO 97/09842, the operation of increasing the distribution uniformity of the resonance mode to support the characteristics of the device will achieve an improvement in the frequency response of the device itself. The member may be made of a material having an isotropic bending rigidity. In this example, the effective length and effective angle are the actual length and the actual angle. In addition, the member may be made of a material which is anisotropic with respect to bending rigidity. In this example, the effective length and effective angle are adjusted to compensate for the non-isotropic actual length and actual angle of the material. The effective length ratio ranges from 1.08: 1 to 1.17: 1, 1.82: 1 to 1.88: 1, or 1.42: 1 to 1.49: 1. The effective angle ranges from 75 to 100 degrees. -6-This paper size is in accordance with Chinese National Standard (CNS) A4 (210 X 297 mm) 5. Description of the invention (4) ::: The shape can be a truncated triangle, so the two sides of the member are: : Go, and connected by a fourth side. The effective angle can be defined between the sides of the angle °. The selection of the ratio of the effective length of the truncated sides can provide the desired frequency distribution. The curvature of each side of the t-plate type I member can be selected to be zero. Here, at least one of the other parameters must be changed to achieve the desired curve: cloth. The member may have two substantially straight sides, and a third = side. The effective angle is defined as the two substantially straight sides—to the evening two or all sides may be Bent. The curved side or its parent may be convex or concave. ^ In a specific embodiment, the third side includes an effective half-touched first arc that intersects the Z center with the two straight lines. This configuration was found by the inventors that y has a better uniform distribution of resonance modes, which can lead to improved sound performance. A The component may be in the shape of a truncated triangle. The truncation can be traced by the second arc of the effective radius r centered on the phase point. The ratio P T of the effective half of the second arc to the effective radius R of the first arc is selected to provide the necessary sacrificial distribution, for example, r: R may be 1: 5. The effective angle θ and the ratio; can be selected to achieve the desired frequency distribution, for example, it can be related according to the following formula: θ = 95-50ρ. The surface? The form member may be substantially in the form of a right triangle. The right angle may or may not be the effective angle. Additional improvements in this frequency distribution can be obtained by combining the present invention with other metrics, such as panel parameters (such as quality, paper dimensions, and paper standards (CNS) and eight iron grids (training) <297 public love) 561788 A7 B7, [Explanation of the invention], so as to reduce the minimum operating frequency of the sound device to improve the reproduction of the bass sound. The sound of the aforementioned sound device and an exciter mounted on it comes here: force: bending The wave energy reaches the sound device to cause the sound device to be distributed :, ',, and is also included in the present invention. By appropriately selecting the frequency, it is distributed to the desired sound output. If a substantially uniform sound is achieved, The knife can be expected to have-a substantially uniform frequency performance (the sound output class L includes the microphone of the sound device as described above, and the conversion device is adapted to respond to the resonance of the panel form due to the incident sound energy. Generate a signal, which is also included in the present invention. Brief description of the drawings Now the invention will be described with reference to the following drawings as an example, in which FIG. 1 shows a party according to the present invention. Was added a sound device architecture of FIG speakers;

P Figure 2 shows the change in the ratio R of the non-uniformity L of the effective length of the two sides of the panel shown in Figure 丨; Figures 3 A and 3B show Frequency f distribution of the resonance mode of the triangular panel with ratios between M3 · '1 and 1.85: 1; Figure 4 shows the ratio of the non-uniformity L of the effective length of the two sides of the panel shown in Figure 1 Variation of R, which is installed by an elastic suspension; Figures 5 A and 5 B are not the frequency f distribution of the resonance mode of a rectangular panel with a ratio of the effective length of the sides of 1.13: 1 and 1.45: 1, respectively. Figure 6 shows the deviation of 90 ° from the angle E in the panel of Figure 1; -8-This paper size applies the Chinese National Standard (CNS) A4 specification (210X 297 public love) 5. Description of the invention (6) Figure 7 does not show the change in center-to-center accuracy of the resonance frequency distribution with the effective angle E; Figures 8A, 8B, and 8C show the effective angle 90, respectively. , 85. and%. The distribution of the frequency f of the resonance mode of the dihedral panel; Figures 9a and 9b show the surface architecture diagram of a sound device according to the other two aspects of the present invention; Figure 10 shows an effective ratio 具有 and effective angle Contour maps of changes in the uniformity of the distribution of the resonance modes of theta; Figures UA, 11B, and lie show effective angles of 45, respectively. ,do not. And 85. The distribution of the frequency f of the resonance mode of the panel of Fig. 9b is shown in Fig. 11d, which has an effective angle of 70. The frequency f distribution of the resonance mode of the panel of Fig. 9b; and Figs. 12a to 12e are plan views of different sound devices according to the present invention. Detailed description of the invention Fig. 1 shows a speaker 1 in the form of a panel, which comprises a panel-shaped component 2 / a converter 5 for exciting the panel to vibrate in a curved wave, thereby generating a sound output. The panel-shaped member 2 is supported by an elastic suspension 3 in a frame 4. The frame 4 and the suspension 3 extend around the panel form member. The panel form member 2 is capable of supporting back-curved wave vibration and has a frequency distribution of a resonant bending wave mode. The position of the converter 5 for exciting the panel-shaped member to the bending wave vibration is selected to be substantially uniformly light-coupled to the resonance bending wave mode, especially the lower-frequency resonance f-curvature mode. The methods used to determine this position are well known and can be found, for example, in the aforementioned W097 / _42, as well as in WO99 / 52324 and W099 / 56497 (herein incorporated by reference). V. Description of the invention (7) In FIG. 1, the panel form member is in the form of a __right angle ⑻ triangle panel. The shape of the triangle is determined by the adjacent 1's opposite sides and the hypotenuses 12,14,16 and the 1 'degree between the adjacent and opposite sides 12'14. According to the first aspect of the present invention, the adjacent and opposite sides The selection of the length ratio can provide the frequency distribution of the desired resonance mode. In particular, the ratio can be selected to minimize the non-uniformity of the resonance mode frequency distribution of the member's buckling wave vibration. By minimizing non-uniformity, there is a greater possibility to evenly couple the converter to the resonance mode at any given location. Therefore, the position of the converter is less important. The uniformity of the frequency distribution of the resonance mode can be expressed as a number of different metrics, see e.g. W099 / 56497 by the inventors. In the figure below, the uniformity is measured by the value L of the least square central difference of the mode frequencies, that is, L = / y ^ (/ w-i + / w ^ = 2 / m) 2 Μ -1 where fm is the m-th mode Frequency (0 &lt; = m &lt; = M). 14 is better than normal, so it is not sensitive to variables other than shape. The normalization may be the product of the panel area or the product of the panel area divided by a reference area. If the panels being compared are made of the same material, adjusting the area will be quite effective. In addition, L can be normalized by multiplying by the mode density. The average mode density is defined by the following formula: dN Area \ μ V-5 where N is the number of modes, μ is the area density of the panel, and B is the panel 561788 A7 _____ B7 V. Description of the invention (8) Bending rigidity: These normalization operations are all equal in effect. Fig. 2 shows the change in the effective length of the adjacent and opposite sides of the panel shown in Fig. 1 in the ratio R to the non-uniformity L. The results obtained from theoretical modeling are assumed to be suspensions with zero rigidity3. Line A represents the non-uniformity (49 · 939) level of the corresponding rectangular panel with an aspect ratio (ie, the ratio of the long side to the short side) of 1 · 134. The aspect ratio of the rectangular panel is equal to the ratio of the two sides of the triangle, which is not the hypotenuse. The uniformity level of the frequency distribution of the two-sided panel is in the range of ^^^^ to 1.17 and N '= 1.82 to 1.88, which is equal to or better than r, which is equal to or equal to The less than A ^ non-uniformity is minimized as shown at "and M," which corresponds to R values substantially equal to 1.13 and 1.85, respectively. Figures 3A and 3B show that the adjacent and opposite sides 12, A histogram of the frequency £ distribution of the resonance mode of the triangular panel of 14 whose proportions are M-1.13 and M '= 1.85. An example of a low uniformity distribution is shown in Figure jm. Figure 3 A and 3B frequencies The distribution is clearly more uniform than in Figure nD. In Figures 3 A and 3B, the resonance mode is substantially uniformly distributed in frequency, that is, the modes are spaced approximately equidistantly along the distribution. Ψ In In practical applications, the panel suspension 3 will have a rigidity range within 500 kN / m. The model of the panel suspension can be performed by adding a spring with a value of 500 kN / m at each edge node, which is limited to out-of-plane The theoretical result of the non-uniformity of the frequency distribution of this panel It is shown in Fig. 4. As shown in Fig. 2, the non-uniformity L has a first minimum value p, which corresponds to R is substantially equal to 1.13. However, 'about at Bu 47, this minimum value will not be as in -11-This paper size applies the Chinese National Standard (CNS) A4 specification (210 χ 297 mm) 561788 A7 —- _ B7_ V. Description of the invention (9) The corresponding minimum value in the zero-rigid embodiment L = It is as low as 40. It can obtain the same or better performance than a corresponding rectangular panel in a range that is slightly narrower than the R range shown in Figure 2. That is, 丨 to 丨 15. It has a second range. Q, the middle R is between 142 and 149, where the non-uniformity is less than or equal to the corresponding rectangular panel. The non-uniformity is minimized at P ', and L is approximately equal to 45, and R is substantially It is equal to 1.45. The range Q ′ and the minimum value P are both lower than the corresponding values of the zero rigid embodiment in FIG. 2. According to the two minimum values p, p, the resonance frequency distribution of the triangular panel is not shown in the figure. 5A and 5B. Again, these can generally be distributed with low uniformity compared to the graph UD. The inventors have also found The deviation of the angle £ of the triangular panel 2 in FIG. 丨 is 90, which can affect the uniformity of the resonance mode distribution. As shown in FIG. 6, the angle E between two adjacent sides 12, 14 can be maintained The length of the side is fixed to change. The non-uniformity of the frequency distribution is measured as described above using the minimum variance parameter L. Figure 7 shows the change in the non-uniformity L of triangles with different angles E. The value of B is normalized and is different from that shown in the previous figure. Fig. 7 shows that by properly selecting the angle E, a desired uniformity of the frequency distribution can be obtained. In particular, non-uniform sentence structure can be minimized by selecting the angle E to about ^ degrees. Similarly, non-uniformities with low values can be obtained by rotating the "trough" by 75 to 100 degrees, because [is not sensitive to angles in this range. A rectangular panel with an effective angle of 90 degrees is the right angle shown in Figure 1, which has the further advantage that it can be used with a small amount of -12-

561788 A7 B7 Fifth, the invention description (10) or a rectangular block without waste. The resonance frequency distribution of a triangular panel with an angle E of 90, 85, and 95 degrees (is an arbitrary frequency unit, which is only for comparison) is shown in Figs. 8A, B, and C, respectively. In each figure, the mode of the resonant bending wave mode is substantially uniformly distributed in frequency. Fig. 9a shows a schematic diagram of a sound device comprising a substantially triangular panel 2 in the form of a section. The panel 2 includes two substantially straight sides 20, 22, each of which has a length R, and defines an angle &amp; (theta) &amp; a third curved side 24. The curved side is a convex curve and is defined by an arc of length R centered at the intersection 26 of the two substantially straight sides. Fig. 9b shows a sound device similar to that of Fig. 9a, so its common features have the same reference numbers. The sound device includes a triangular panel 2 carried. The shape is similar to the panel of Figure 9a, but with the top portion removed. The truncated angle (or tip portion) is defined by the second arc 28 with an effective radius of 1 ^ around the intersection. The ratio P = r / R has been found to determine the sound performance of the resulting device. In a preferred embodiment, the outer diameter r of the central section 28 is approximately less than 5 times the radius R of the arc 24, that is, ρ == 0. In addition to selecting the value P for -it, the angle e (theta) between the two f sides that are flat sides can be selected to provide the desired frequency distribution. Figure 10 shows the ratio rh. And the non-uniformity of the resonance mode of the internal angle theta

As described above, L is measured by the least square center difference of the frequency of this mode, and assumes zero rigid suspension for modelling. X is comparable to that shown in Figure 9a and the parameter values can be selected to provide a frequency distribution of -13.

561788 A7 B7 V. Description of Invention (11) Rectangular panels with equal area and an aspect ratio of 1 · 134 should be more uniform. Therefore, this parameter value can be selected to provide a value L less than 47. For the specific embodiment of Fig. 9a, 0 = 0 !, and l is the minimum for s, which is approximately equal to 45, 55, and 85 to 90 degrees. For the preferred embodiment of Fig. 9b, ρ = 0.2 and L minimizes θ in the range of 81 to 86 degrees. In general, the minimum value of 'L is essentially following a trend line of 0 = 95_50. The resonance frequency distributions of the panels at angles 45, 55, and 85 to 90 degrees of Fig. 9a are shown in Figs. 11A, B, and C, respectively. For comparison, Figure iiD shows the low uniformity distribution of a panel, where θ = 70. And p = (M. As shown in FIG. 10, the numerical value L of this panel is greater than 60. The frequency distribution of the graph iid is not uniform for several pattern clusters at about 2000 Hz, 40001, and the like. In contrast, the frequency distributions of Figures A, 1B, and 1 are substantially uniform. The above examples are about isotropic panel materials, where the effective length and angle f correspond to the actual length and angle of the panel. When The material of the panel is non-isotropic, or more specifically, it is orthogonal (having two rigid orthogonal axes). The actual length and angle of the beta panel are different from the effective length and angle, because The stiffness of the material is related to the direction. The calculation of the actual size of a panel first involves establishing the difference between the orthogonal directions of the rigidity of the orthogonal material = difference, and the main direction of the nodal lines of an equal orthogonal panel ( The calculation system uses, for example, finite element analysis.) Then, the rigid 1 ± direction of the orthogonal material is decomposed into the main direction of the node line. In each direction, the 1-knife solution is applied to each of the rigidity of the non-isotropic panel. Ratio of rigidity in each direction: used to Compensate the panel size in the same direction, so as to achieve the actual size to provide the necessary uniformity of the frequency distribution. The following relationship is 297 mm. In the grid (21〇: -14 A7 _ B7___ _ V. Description of the invention ( 12) The system is used for compensation: B / X4 = constant, where B is the bending rigidity of the panel along each direction, and χ is the actual length of the panel. Please refer to the following examples: One has actual lengths of L1 and L2 The panel is made of an orthogonal material, which has bending rigidity B 丨 and B2 in the direction orthogonal to the rigidity. The effective length u of the panel with bending rigidity B3 made of an isotropic material, and L2 , Is calculated as follows: 1 · The rigidity direction of the orthogonal material is decomposed into the main direction of the node line to provide the bending rigidity B1, and B2, 2. 2. Bl / B3 = 16 and B2 / B3 = l, that is, the application relationship B / χ4 = constant. Therefore, 2L1 = L1 and L2 '= L2. In other words, the effective lengths of the two sides L1, and L2 are the actual lengths of the two corresponding sides. L1 and one and a half of the actual length L2. And the main direction of the node line is the known conceptual axis The concept of frequency is the frequency of the beam having the same length of the shaft concept. The compensation relationship by a superscript in a resonance mode of the frequency fn formula obtained, i.e.,

Bazhong B is the author Qugang Sheng, μ is the area density, χ is the standard length, and λ is a constant, which is based on the pattern of the number of units in other $ numbers on a particular concept axis model The frequency is therefore proportional to the square root of the -curve stiffness along the axis and inversely proportional to the actual length along the axis. ~ • 15-

561788 A7 B7 V. Explanation of the invention (13) For the orthogonal panel, μ is fixed and the value of B is B1 along one axis and B2 along the vertical axis. The axes are each equal to a beam of length LWL2. The interleaving of the modes along these two axes is key, in particular, it can help to keep the frequency ratio of each axis constant constant. By rearranging the following equation (that is, the frequency ratio), we can get the compensation relationship. / 1/2. Ά2 IW Έ)] IB2:

C Assembly Figures 12a to 12e show different panel shapes. In Figs. I2a and i2c, all three sides of the panel 2 are curved. In the figure, two side edges% are convex curves, and one side edge 32 is a concave curve, so the panel has a sail-like shape. In Fig. 12c, three sides 33 are concave curves, so the panel has an epicycloid geometry. In Fig. 12b, the panel 2 is in the form of a truncated triangle of the truncated sides 34 connected by a concave curve 36; therefore, the concave curve 36 defines the truncated angle. In Fig. 12d, the panel 2 is generally similar to Figs. 9a and 9b, except that the curved side edge 38 is defined by an ellipse, and its center is at the intersection of the two straight side edges 40. The panel 2 may or may not be truncated by a dotted line 42 defining the selective truncation. The dotted line 42 is also an ellipse, and its center is located at the intersection. In Fig. 126, the panel has a single straight side edge 40, and the other two sides are curved to form a continuous parabola curve 42 having a tip or dot 44. -16- This paper size applies Chinese National Standard (CNS) A4 specification (210X297 mm) 561788 A7 B7 V. Description of the invention (14) Reference number · Serial number reference 1 Panel form speaker 2 Panel 3 Suspension 4 Frame 5 Converter 10 Angle 12 Adjacent side 14 Opposite side 16 Beveled side 20 Side 22 Side 24 Arc 26 Intersect 28 Center section 30 Protruded curved side 32 Recessed curved side 34 Cut off side 36 Curved side 38 Elliptical side edge 40 Straight side edge 42 Elliptical truncated angle 44 Parabolic curve 46 Dot -17 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm)

Claims (1)

561788 Patent application range 2. 3. 4. 5. 6. 7. A sound device includes a panel-shaped member that can support bending wave vibration and has a frequency distribution of a resonant bending wave mode, which is essentially The triangular form of the component can provide a desired frequency distribution of the resonance mode, where at least one of the parameters is determined by the effective length ratio of the two sides of the triangular form, and at least one of the triangular forms. The effective angle between the two sides and the curvature of at least one side are selected. For example, the sound device of claim 1 of the patent scope, wherein the parameter is selected to minimize non-uniformity in the frequency distribution. If the sound device of the scope of patent application 1 is made of a material whose bending rigidity is isotropic, the effective angle is the actual length and the actual angle. The sound device of the scope of patent application 1 is anisotropic at a flexural rigidity Made of material, and the effective length and the effective angle are adjusted to compensate the anisotropy of the material for the actual length and actual angle. If the sound device of the scope of patent application 1 item, the range of the ratio is 1.08 ·· 1 to 丨 · 丨 7 ·· J &lt; If the sound device of the scope of patent application item 5 is 1 · 11: 1 to 1.1 5: 1 . For example, the sound device in the scope of patent application No. 6 is equal to 1.13: 1. For example, the sound device of the scope of patent application No. 5 is made of an isotropic bending rigid material in which the member is formed by the effective length and the member is formed by the ratio of the effective length of the ratio. Wherein, the ratio is essentially the component length of the effective length and the 18 X 297 mm) 8. The effective angle of the scope of patent application is the actual length and actual angle. 9. The sound device as claimed in item 5 of the scope of the patent application, wherein the component is made of a material which is non-isotropic with respect to deflection rigidity, and the effective length and the effective angle are adjusted to compensate the material Anisotropic actual length and actual angle. ^ 10. The sound device according to item 丨 of the patent application range, wherein the range of the ratio of the effective length is 1.82: 1 to 1.88: 1. 11. The sound device as claimed in claim 10, wherein the ratio is substantially equal to 1.85: 1. 12. The sound device as described in the full-time enquiries, where the component is made of a material that is isotropic to the bending rigidity, and the effective length and the effective angle are the actual length and the actual angle. 13. If the sound device of the scope of application for patent No. 10, the component is made of a material that is non-isotropic to bending rigidity, and the effective length and the effective angle are adjusted to compensate for the non-equivalence of the material. Anisotropic actual length and actual angle. 14. The sound device according to item 丨 of the patent application range, wherein the range of the ratio of the effective length is 1.42: 1 to 1.49: 1. 15. The sound device according to item 14 of the patent application, wherein the ratio is substantially equal to 1.45: 1. 16. The sound device according to item 14 of the scope of patent application, wherein the component is made of a material that is isotropic with respect to bending rigidity, and the effective length and the effective angle are actual length and actual angle. 17. If the sound device according to item 14 of the scope of patent application, the component is made of a material whose scope of patent application is 561788 A8 B8 C8 D8 and whose rigidity is anisotropic, and the effective length and the effective angle To adjust the actual length and actual angle to compensate for the anisotropy of the material. Wherein the effective angle is in which the effective angle is in which the effective angle is in which the effective length is in which the effective length in which the member is a section of each of the members in which the member has two 18? The range of the sound device of the first patent application range is 75 to 100 degrees. 19. The sound device according to item 18 of the scope of patent application is 85 degrees in quality. 20. The sound device such as item 18 of the scope of patent application is 90 degrees in quality. 21 · Sound device according to item 18 of the scope of the patent application The ratio ranges from 1.08: 1 to 1.17: 1. 22 · Sound device as claimed in item 18 of the patent application The range of this ratio is 1.82: 1 to 1.88: 1. 23. · Sound device such as item 18 of the scope of patent application The ratio ranges from 1.42: 1 to 1.49: 1. 24. The triangular form of the corner of the sound device as in the scope of patent application item 1. 25. The side of the sound device according to the scope of patent application is curved. 26. The sound device according to item 1 of the patent application has a substantially straight side and a third curved side, and the effective angle is defined between the two substantially straight sides. 27. The sound device of claim 26, wherein the effective angle is 45, 54, 90, or 95 degrees. -20-w. Patent application park For example, the sound device of claim 26 of the patent scope, wherein the third side contains the first arc of the effective radius rule centered on the intersection of the two straight lines. 29. The sound device of claim 28, wherein the shape of the member is a truncated triangle. 30. The sound device of claim 29, wherein the truncated angle is defined by the second arc of the effective radius Γ centered on the phase parent point. 31. The sound device of claim 30, wherein the ratio ρ of the effective radius r of the second arc to the effective radius R of the first arc is selected to provide the desired frequency distribution. 32. The sound device of claim 31, wherein the effective half-duty Γ of the second arc is approximately less than $ times the effective radius R of the first arc. 33. For a sound device according to item 31 of the scope of patent application, wherein the effective angle and the ratio ρ are substantially based on the relationship θ = 95 ° 0ρ. 34. A sound device comprising a panel opening &gt; -type member 'that can support bending wave vibration and has a frequency distribution of a resonant bending wave mode, the member is substantially triangular and has two substantially flat , A third curved side, and an effective angle defined between the two substantially straight sides. 35. The sound device of claim 34, wherein the effective angle is selected to minimize non-uniformity in the frequency distribution. 36. The sound device according to item 34 of the scope of patent application, wherein the third side includes the first -21 of the effective radius R centered on the intersection of the two flat straight lines-This paper size applies the Chinese National Standard (CNS ) A4 specification (210X297 male 561788 ABCD patent application arc 37. Sound device such as patent application item 36, wherein the shape of the component is a triangle with a truncated angle, and the truncated angle is centered on the intersection point Defined by the second arc of the effective radius Γ 38. The sound device according to item 37 of the patent application, wherein the ratio p of the effective radius r of the second arc to the effective radius R of the first arc is selected to provide the desired 39. A speaker comprising a sound device comprising a panel-shaped member capable of supporting bending wave vibration and having a frequency distribution of a resonant bending wave mode, the member being substantially triangular in form, The selection of the parameters of the component can provide a frequency distribution of the desired resonance mode, wherein at least one of the parameters is determined by the two sides of the triangle form. Selected from the effective length ratio, the effective angle between at least two sides of the triangular form, and the curvature of at least one side, and a converter coupled to apply bending wave energy to the panel form member to cause the Panel-shaped components resonate and generate a sound output. '40. The speaker of item 39 of the patent application, wherein the parameter is selected to minimize non-uniformity in the frequency distribution. 41. A microphone, which Contains a sound device, which includes a panel-shaped member that can support bending wave vibration and has a frequency distribution of a resonant bending wave mode. The member is a substantially triangular shape. This paper is compliant with Chinese National Standards (CNS ) A4 specification (210X297 mm) ~ &quot; ---- 561788 A8 B8 C8 D8, patent application form, the selection of the parameters of this component can provide a desired frequency distribution of the resonance mode, where At least one is determined by the effective length ratio of the two sides of the triangular form, the effective length between the at least two sides of the triangular form And at least one side is selected from the curvature, and a converter is coupled to generate a signal in response to the resonance of the panel-shaped member of the incident sound energy. ) A4 size (210 X 297 mm)