Sound insulation panel

Abstract

To provide a lightweight sound insulating panel having high sound insulating performance.SOLUTION: In the sound insulation panel 1 including the concavo-convex structure 2, a thickness T of a member constituting the concavo-convex structure 2 is 0.1 mm or more and 20 mm or less, a tensile modulus of elasticity of the member constituting the concavo-convex structure 2 is 0.1 GPa or more, a product of a primary resonance frequency f [Hz] of out-of-plane vibration of the sound insulation panel 1 and a side length L [m] is 80 [Hz·m] or more. A quotient of a height H [m] from the lowest part to the highest part of the uneven structure 2 and a side length L [m] is 0.01 or more and 0.7 or less, and a projected area ratio of a projected area excluding the uneven structure 2 to the whole projected area projected in the thickness direction is less than 20%.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to an acoustical panel. [Background technology]

[0002] There is an increasing demand for noise insulation performance in partitions between buildings and the exterior in order to improve the indoor environment in buildings and the interior environment in vehicles. Sound transmission loss is an indicator of sound insulation performance in partitions between buildings and the exterior. Sound transmission loss represents the reduction in the energy of transmitted sound relative to incident sound on a sound-insulating panel placed in a partition, with a higher value indicating higher sound insulation performance. When the material used for a sound-insulating panel is a homogeneous monolithic material, sound transmission loss is primarily determined by mass, and exhibits a characteristic of decreasing values, particularly near the primary resonance frequency of the in-plane vibration of the sound-insulating panel. Furthermore, when the material used for a sound-insulating panel is a homogeneous monolithic material, the frequency range lower than the primary resonance frequency of the in-plane vibration is called the rigidity law region, the frequency range higher than the primary resonance frequency of the in-plane vibration is called the resonance region, and the frequency range higher than the resonance region is called the mass law region. In the rigidity law region, the rigidity of the material used for the sound-insulating panel and the rigidity conditions of the sound-insulating panel's boundaries affect sound transmission loss, and improving rigidity tends to increase sound transmission loss. In the resonance region, the resonance of the vibration modes of the sound-insulating panel due to the energy of the transmitted sound affects sound transmission loss, resulting in peaks and dips in sound transmission loss depending on the vibration mode of the sound-insulating panel. In the mass law region, the greater the mass (surface density) of the material used in the soundproofing panel, the greater the sound transmission loss, and the sound transmission loss tends to decrease around a certain frequency due to the coincidence effect caused by the bending vibration of the soundproofing panel.

[0003] For example, when aluminum plates, which are homogeneous single-layer materials, are used as sound-insulating panels placed in partitions between buildings and the outside, the aluminum plates' sound-insulating performance in the audible range can be improved by increasing their mass (area density). However, when a panel with a large mass (area density) is used, while sound-insulating performance in the audible range can be improved, the handling of the panel and the durability of the partition become less favorable. Furthermore, when a panel with a large mass (area density) is used, sound-insulating performance tends to decrease as the frequency decreases, according to the mass law. Therefore, in order to improve sound insulation performance in the low frequency range, it has been proposed to form a membrane member, which is part of a sound insulation panel, into a shape with curvature, and to improve sound insulation performance by insulating sound through the elastic repulsive force caused by in-plane expansion and contraction (see, for example, Patent Document 1).It has also been proposed to improve sound insulation performance by using a membrane member to generate in-plane expansion and contraction and providing beams to increase rigidity (see, for example, Patent Document 2). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 4227618 [Patent Document 2] Patent No. 4024272 Summary of the Invention [Problem to be solved by the invention]

[0005] However, in structures that insulate sound by the elastic repulsive force of in-plane expansion and contraction, the rigidity of the material must be low to generate in-plane expansion and contraction, which has the drawback of narrowing the frequency range that can be insulated. Furthermore, in structures that use membrane members to generate in-plane expansion and also provide beams to increase rigidity, the weight is increased. Furthermore, a new problem was discovered: the flat, non-curved parts that make up the sound-insulating panel vibrate, reducing sound-insulating performance.

[0006] In view of the above circumstances, an object of the present invention is to provide a sound-insulating panel that is lightweight and has high sound-insulating performance. [Means for solving the problem]

[0007] As a result of intensive research to achieve the above object, the inventors have discovered that an increase in the primary resonance frequency of out-of-plane vibration contributes to improved sound insulation performance in sound-insulating panels. They have also discovered that a lightweight sound-insulating panel with high sound insulation performance can be obtained by using a highly rigid material, having a specific uneven structure, and having a ratio of the projected area excluding the uneven structure to the total projected area projected in the thickness direction equal to or less than a certain value. Based on this finding, the inventors have conducted further research and have completed the present invention.

[0008] The present invention has been made to solve the above problems, and the gist of the present invention is as follows. [1] A sound-insulating panel having a concave-convex structure, wherein the thickness T of the members constituting the concave-convex structure is 0.1 mm or more and 20 mm or less, the tensile modulus of elasticity of the members constituting the concave-convex structure is 0.1 GPa or more, the length of the side of a square whose area and projected area are the same is defined as the side length L, the product of the primary resonance frequency f [Hz] of the out-of-plane vibration of the sound-insulating panel and the side length L [m] is 80 [Hz·m] or more, the quotient of the height H [m] from the lowest to the highest part of the concave-convex structure and the side length L [m] is 0.01 or more and 0.7 or less, and the ratio of the projected area excluding the concave-convex structure to the total projected area projected in the thickness direction is less than 20%. [2] The sound-insulating panel according to [1], wherein the members constituting the uneven structure are metal or resin. [3] The sound-insulating panel according to [1] or [2], wherein the uneven structure is singular. [4] The sound-insulating panel according to any one of [1] to [3], wherein the concave-convex structure has a plurality of curved surface portions with different curvatures. [5] The surface density of the members constituting the sound-insulating panel is 200 kg / m 3 More than 12,000kg / m 3The sound-insulating panel according to any one of [1] to [4] below. [Effects of the Invention]

[0009] According to the present invention, it is possible to provide a sound-insulating panel that is lightweight and has high sound-insulating performance. [Brief explanation of the drawings]

[0010] [Figure 1] FIG. 1(a) is a plan view of a sound-insulating panel according to an embodiment of the present invention, FIG. 1(b) is a cross-sectional view taken along line AA in FIG. 1(a), and FIG. 1(c) is a schematic perspective view of the sound-insulating panel according to an embodiment of the present invention. [Figure 2] FIG. 2(a) is a plan view of a sound-insulating panel according to an embodiment of the present invention, FIG. 2(b) is a cross-sectional view taken along line BB in FIG. 2(a), and FIG. 2(c) is a schematic perspective view of the sound-insulating panel according to an embodiment of the present invention. [Figure 3] FIG. 3(a) is a plan view of a sound-insulating panel according to an embodiment of the present invention, FIG. 3(b) is a cross-sectional view taken along line CC in FIG. 3(a), and FIG. 3(c) is a schematic perspective view of the sound-insulating panel according to an embodiment of the present invention. [Figure 4] FIG. 10 is a plan view of a sound-insulating panel as a comparative example. [Figure 5] 10 is a graph showing the results of subtracting the mass law calculated from the surface density for each frequency of the sound-insulating panels according to Examples 1 and 2 and Comparative Examples 1 and 2. DETAILED DESCRIPTION OF THE INVENTION

[0011] As shown in Fig. 1, a sound-insulating panel 1 according to an embodiment of the present invention has a concave-convex structure 2. In the sound-insulating panel 1 according to an embodiment of the present invention, the thickness T of the members constituting the concave-convex structure 2, the tensile modulus of elasticity of the members constituting the concave-convex structure 2, the side length L being the length of a side of a square having the same projected area as the area of ​​the sound-insulating panel 1, the product (f × L) of the primary resonance frequency f [Hz] of the out-of-plane vibration of the sound-insulating panel 1 and the side length L [m], and the quotient (H / L) of the height H [m] from the lowest to highest point of the concave-convex structure 2 and the side length L [m] satisfy specific conditions. Furthermore, the sound-insulating panel 1 satisfies the condition that the ratio of the projected area excluding the concave-convex structure to the entire projected area of ​​the sound-insulating panel 1 projected in the thickness direction is equal to or less than a certain value. When the sound-insulating panel 1 according to an embodiment of the present invention satisfies these specific conditions, the rigidity of the sound-insulating panel 1 is increased, and vibrations due to in-plane elastic expansion and contraction deformation are suppressed to 20 kHz or higher, which is outside the range of human hearing. This reduces the energy consumption of transmitted sound due to in-plane vibration, while increasing the energy consumption of transmitted sound due to out-of-plane vibration, resulting in a lightweight sound-insulating panel with high sound-insulating performance.

[0012] By providing the sound-insulating panel 1 with the uneven structure 2, the rigidity of the top of the uneven structure 2 is improved, and when the energy of transmitted sound passes through the sound-insulating panel 1, the top and bottom of the uneven structure 2 function as fixed ends, inducing out-of-plane vibrations consisting of components that vibrate perpendicularly (out-of-plane) to the sound-insulating panel, and out-of-plane vibrations occur near the bottom, which has relatively low rigidity. In other words, by providing the sound-insulating panel 1 with the uneven structure 2, the rigidity of the entire sound-insulating panel 1 is improved, in-plane elastic expansion and contraction deformation is suppressed, and excessive out-of-plane vibrations can also be suppressed. When the thickness T of the members constituting the uneven structure 2 of the sound-insulating panel 1, the tensile modulus of elasticity of the members constituting the uneven structure 2, the product of the first resonance frequency f of the out-of-plane vibration of the sound-insulating panel and the side length L, and the quotient of the height H of the uneven structure 2 and the side length L satisfy certain conditions, it becomes possible to suppress in-plane elastic expansion and contraction deformation up to audible frequencies and to suppress out-of-plane vibration up to the first resonance frequency, thereby improving the decline in sound-insulating performance across all frequency ranges, especially in the low frequency range (100 to 400 Hz). Furthermore, by satisfying the condition that the ratio of the projected area excluding the uneven structure to the total projected area of ​​the sound-insulating panel 1 projected in the thickness direction is equal to or less than a certain value, it becomes possible to suppress vibrations caused by the flat, non-curved parts that make up the sound-insulating panel, thereby improving the decline in sound-insulating performance across all frequency ranges, particularly in the low-frequency range (100 to 400 Hz).

[0013] As shown in FIGS. 1(a) to 1(c), a sound-insulating panel 1 according to an embodiment of the present invention has a concave-convex structure 2 composed of a first curved surface portion 2A and a second curved surface portion 2B, and a flat surface portion 3 at the periphery. The first curved surface portion 2A is a curved portion extending from the periphery of the sound-insulating panel 1 to the second curved surface portion 2B at the center, with a curvature in the thickness direction (Z-axis direction). As shown in FIGS. 1(a) and 1(c), the first curved surface portion 2A is formed by four portions extending from the four sides of the periphery of the sound-insulating panel 1, which are joined together without any gaps to form the concave-convex structure 2. The second curved surface portion 2B has a curvature in the thickness direction (Z-axis direction) similar to the first curved surface portion 2A, but has a different curvature from the first curved surface portion 2A, being a portion having a smaller curvature than the first curved surface portion 2A. In the concave-convex structure 2 of the embodiment shown in FIG. 2, the second curved surface portion 2B forms the apex of the concave-convex structure 2. In FIG. 1(a), the shape of the first curved surface portion 2A when viewed in the thickness direction is circular, but it may be other shapes, or may be polygonal such as quadrangle.

[0014] One sound-insulating panel 1 may be provided with one or more uneven structures 2, but from the viewpoint of efficiently converting the energy of transmitted sound into energy that induces out-of-plane vibration, it is preferable that there is one uneven structure 2. A plurality of sound-insulating panels 1 can be arranged adjacent to each other to form a sound-insulating structure such as a soundproof wall.

[0015] The uneven shape of the uneven structure 2 refers to a hollow shape that protrudes from one surface 1A of the sound-insulating panel 1 or the opposite surface 1B, for example, a hemispherical shape consisting of a curved surface formed by a first curved surface portion 2A and a second curved surface portion 2B, as shown in Figures 1(b) and 1(c). The uneven structure 2 need only have an uneven shape overall, and does not need to be a seamless curved surface, but may be formed as a polyhedron, or may have locally raised or recessed portions, or may have locally varying curvatures.

[0016] The concave-convex structure 2 is not limited to the form shown in FIG. 1, and may have any shape as long as it can efficiently convert the energy of transmitted sound into energy that induces out-of-plane vibration. For example, the concave-convex structure 2 may be configured only by first curved portions 2A, as shown in Figures 2(a) to 2(c). In the concave-convex structure 2 of the embodiment in Figure 2, first curved portions 2A having a curvature in the thickness direction (Z-axis direction) from the peripheral portion of the sound-insulating panel 1 extend to the center of the sound-insulating panel 1, and a collection of the first curved portions 2A forms the apex 2C of the concave-convex structure 2. In other words, the concave-convex structure 2 of the embodiment in Figure 2 has a generally pyramidal shape with flat portions 3 on all four sides as the bottom surface. 3(a) to 3(c), the concave-convex structure 2 has a substantially hemispherical first curved surface portion 2A that has a curvature in the thickness direction (Z-axis direction) from the peripheral portion of the sound-insulating panel 1. In other words, the concave-convex structure 2 of the embodiment in Fig. 3 has a substantially dome shape with flat portions 3 on all four sides as the bottom surface.

[0017] The thickness T of the members constituting the concave-convex structure 2 is 0.1 mm or more and 20 mm or less. If the thickness T of the members constituting the concave-convex structure 2 is less than the above lower limit, the mechanical rigidity of the concave-convex structure 2 cannot be obtained. On the other hand, if the thickness T of the members constituting the concave-convex structure 2 exceeds the above upper limit, it becomes difficult to convert the energy of transmitted sound into energy that induces out-of-plane vibration. From the viewpoints of maintaining mechanical rigidity, contributing to weight reduction, and enabling the energy of transmitted sound to be efficiently converted into energy that induces out-of-plane vibration, the thickness T of the members constituting the concave-convex structure 2 is preferably 0.2 mm or more and 15 mm or less, more preferably 0.5 mm or more and 10 mm or less, and even more preferably 1 mm or more and 5 mm or less.

[0018] The tensile modulus of the members constituting the concave-convex structure 2 is 0.1 GPa or more. If the tensile modulus of the members constituting the concave-convex structure 2 is less than the above lower limit, the in-plane elastic expansion and contraction deformation of the concave-convex structure 2 is not suppressed, and the energy of the transmitted sound induces in-plane vibration, but does not induce out-of-plane vibration. When the tensile modulus of the members constituting the concave-convex structure 2 is equal to or greater than the above lower limit, the in-plane elastic expansion and contraction deformation of the concave-convex structure 2 is suppressed, and the energy of the transmitted sound does not induce in-plane vibration, but the energy of the transmitted sound is efficiently induced into out-of-plane vibration. From the viewpoint of this, the tensile modulus of the members constituting the concave-convex structure 2 is preferably 1 GPa or more, more preferably 5 GPa or more, and even more preferably 10 GPa or more. The upper limit of the tensile modulus of the members constituting the concave-convex structure 2 is not particularly limited, but 500 GPa is a practical upper limit. The tensile modulus of elasticity of the members constituting the concave-convex structure 2 can be measured by a method conforming to JIS K 7161-1:2014.

[0019] The primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1 is preferably 100 Hz or more and 8,000 Hz or less, more preferably 200 Hz or more and 7,000 Hz or less, and even more preferably 300 Hz or more and 6,000 Hz or less. The primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1 can be measured by a method conforming to JIS C 60068-2-81:2007.

[0020] The length of a side of a square whose projected area is the same as the area of ​​the sound-insulating panel 1 (the area on the XY plane in FIG. 1) is defined as side length L. In this specification, the shape of the sound-insulating panel 1 is not limited, and attention is focused on the area of ​​the sound-insulating panel 1, assuming a virtual square whose area is the same as the area of ​​the sound-insulating panel 1, and the length of one side of that square is considered to be side length L. However, when the sound-insulating panel 1 is a square as shown in FIG. 1(a), side length L is defined as the length of one side of the square formed by the sound-insulating panel 1. The product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1 and the side length L is 80 Hz·m or more. If the product (f × L) of the primary resonance frequency f and the side length L is less than 80 Hz·m, it becomes difficult to convert the energy of transmitted sound into energy that induces out-of-plane vibration. From the viewpoint of being able to efficiently convert the energy of transmitted sound into energy that induces out-of-plane vibration, the product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1 and the side length L is preferably 100 Hz·m or more, more preferably 125 Hz·m or more, and even more preferably 150 Hz·m or more. There is no particular upper limit to the tensile modulus of elasticity of the members that make up the concave-convex structure 2, but 2,500 Hz·m is a practical upper limit.

[0021] The height H (Z-axis direction in Figure 1) of the uneven structure 2 is preferably 0.01 m or more and 0.2 m or less, more preferably 0.02 m or more and 0.17 m or less, and even more preferably 0.03 m or more and 0.15 m or less, from the viewpoint of maintaining the rigidity of the top 20 of the uneven structure 2 while making it easier for out-of-plane vibrations to occur near the bottom 21. The height H of the concave-convex structure 2 refers to the height from the lowest part to the highest part of the concave-convex structure 2, specifically the height from the lowest point (for example, the bottom of a recess) of the concave-convex structure 2 to the highest point (for example, the top of a protrusion) of the concave-convex structure 2. When there are multiple concave-convex structures 2, the height H with the largest value is used.

[0022] The quotient (H / L) of the height H and the side length L of the concave-convex structure 2 is 0.01 or more and 0.7 or less. If the quotient of the height H and the side length L of the concave-convex structure 2 is outside the above range, it becomes difficult to maintain mechanical rigidity while contributing to weight reduction and to efficiently convert the energy of transmitted sound into energy that induces out-of-plane vibration. From the viewpoint of maintaining mechanical rigidity while contributing to weight reduction and being able to efficiently convert the energy of transmitted sound into energy that induces out-of-plane vibration, the quotient of the height H and the side length L of the concave-convex structure 2 is preferably 0.05 or more and 0.6 or less, more preferably 0.07 or more and 0.5 or less, and even more preferably 0.1 or more and 0.4 or less.

[0023] The surface density of the uneven structure 2 is 200 kg / m 2 More than 8,000kg / m 2 It is preferable that the saturation is 400 kg / m or less. 2 More than 6,000kg / m 2 More preferably, it is 600 kg / m or less. 2 More than 4,000kg / m 2 It is more preferable that the surface density of the concave-convex structure 2 is within the above range, which can contribute to weight reduction while maintaining mechanical rigidity. The surface density of the concave-convex structure 2 can be measured by a method in accordance with JIS Z 8807:2012.

[0024] The ratio R of the projected area A2 excluding the concave-convex structure 2 to the entire projected area A1 projected in the thickness direction (Z-axis direction) of the sound-insulating panel 1 is less than 20%. 2 ] is the projected area of ​​the combined portion of the concave-convex structure 2 and the flat portion 3, and the projected area A2 [m 2Since A2 / A1 is the projected area of ​​the flat portion 3, the projected area ratio R [%] can be calculated by the formula R = A2 / A1 × 100. If the projected area ratio R is 20% or more, vibrations will occur due to the flat portions of the sound-insulating panel 1 that have no curvature, and sound insulation performance will decrease across all frequency ranges, particularly in the low frequency range (100 to 400 Hz). From the viewpoints of making it possible to suppress vibrations due to the flat portions of the sound-insulating panel 1 that have no curvature and improving the decrease in sound insulation performance across all frequency ranges, particularly in the low frequency range (100 to 400 Hz), the projected area ratio R is preferably less than 20%, more preferably less than 18%, and even more preferably less than 16%.

[0025] The members constituting the concave-convex structure 2 are not particularly limited as long as they have mechanical rigidity and are airtight to improve sound insulation performance, and examples thereof include metal plates made of metals such as aluminum plates, steel plates, stainless steel plates, and iron plates, as well as inorganic materials such as glass plates. Examples of the members constituting the concave-convex structure 2 include organic materials such as resin plates containing at least one of polycarbonate resin, acrylic resin, acrylonitrile-butadiene-styrene resin (ABS resin), polypropylene resin, vinyl chloride resin, and epoxy resin. Composite materials such as ceramic plates, gypsum plates, and FRP plates can also be used as the members constituting the concave-convex structure 2.

[0026] Although the embodiments of the present invention have been described above, the present invention is not limited to these examples, and it goes without saying that the present invention can be embodied in various forms without departing from the spirit of the present invention. [Example]

[0027] Hereinafter, the embodiments of the present invention will be described in more detail based on examples, but the present invention is not limited to these examples.

[0028] (Measurement of sound transmission loss) The sound transmission loss of the sound-insulating panels according to the examples and comparative examples was calculated in accordance with JIS A 1441-1:2007. Specifically, a reverberation chamber and an anechoic chamber were partitioned with samples of the sound-insulating panels according to the examples and comparative examples (those with a concave-convex structure were placed so that the convex parts faced the reverberation chamber), and 100 dB of noise was generated from a speaker in the reverberation chamber. The average sound pressure level in the reverberation chamber and the sound intensity in the anechoic chamber at a point 10 cm away from the sound-insulating panels according to the examples and comparative examples were measured, and the sound transmission loss for each 1 / 3 octave band was calculated. The results of subtracting the mass law calculated from the surface density for each frequency from the calculated sound transmission loss for each 1 / 3 octave band are shown in the graph in Figure 5.

[0029] [Example 1] An epoxy resin dome (0.4 m length × 0.4 m width × 0.11 m height × 2 mm thickness) was used as the sound-insulating panel 1 (see FIG. 1 ) having a single uneven structure 2. Table 1 shows the results of measuring the tensile modulus of elasticity of the members constituting the uneven structure of the sound-insulating panel of Example 1, the surface density of the uneven structure, and the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1, as well as the results of calculating the product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel and the side length L, the results of calculating the quotient of the height H of the uneven structure and the side length L, and the projected area ratio of the projected area of ​​the flat portion to the entire projected area.

[0030] [Example 2] An epoxy resin dome (0.4 m long x 0.4 m wide x 0.11 m high x 2 mm thick) was used as sound-insulating panel 1 (see Figure 3) having a single uneven structure 2 consisting only of curved surfaces. Table 1 shows the results of measuring the tensile modulus of elasticity of the members constituting the uneven structure of the sound-insulating panel of Example 2, the surface density of the uneven structure, and the primary resonance frequency f of the out-of-plane vibration of sound-insulating panel 1, as well as the results of calculating the product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel and the side length L, the results of calculating the quotient of the height H of the uneven structure and the side length L, and the projected area ratio of the projected area of ​​the flat portion to the total projected area.

[0031] [Comparative Example 1] An epoxy resin flat plate (length 0.4 m × width 0.4 m × thickness 2 mm) was used as the sound-insulating panel 1 (see FIG. 4(a)) consisting only of the flat portion 3. Table 1 shows the results of measuring the tensile modulus of elasticity, surface density, and primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel 1 according to Comparative Example 1, as well as the results of calculating the product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel and the side length L, the results of calculating the quotient of the height H of the concave-convex structure and the side length L, and the ratio of the projected area of ​​the flat portion to the total projected area.

[0032] Comparative Example 2 An epoxy resin dome (0.4 m long x 0.4 m wide x 0.11 m high x 2 mm thick) was used as sound-insulating panel 1 (see Figure 4(b)) having a single hemispherical uneven structure 2 consisting of flat and curved portions. Table 1 shows the results of measuring the tensile modulus of elasticity of the members constituting the uneven structure of the sound-insulating panel of Comparative Example 2, the surface density of the uneven structure, and the primary resonance frequency f of the out-of-plane vibration of sound-insulating panel 1, as well as the results of calculating the product of the primary resonance frequency f of the out-of-plane vibration of the sound-insulating panel and the side length L, the results of calculating the quotient of the height H of the uneven structure and the side length L, and the projected area ratio of the projected area of ​​the flat portion to the total projected area.

[0033] [Table 1]

[0034] From the graph shown in FIG. 5, Example 1 showed an improvement of up to 16 dB in sound transmission loss at specific frequencies (approximately 100 to 630 Hz) compared to Comparative Example 1. Example 1 showed an improvement of up to 16 dB in sound transmission loss at specific frequencies (approximately 315 to 1,250 Hz) compared to Comparative Example 2. Example 2 showed an improvement of up to 15 dB in sound transmission loss at specific frequencies (approximately 100 to 800 Hz) compared to Comparative Example 1. Example 2 showed an improvement of up to 19 dB in sound transmission loss at specific frequencies (approximately 315 to 1,000 Hz) compared to Comparative Example 2. In Comparative Example 1, the primary resonance frequency is increased, so sound insulation performance at low frequencies is greatly improved, but the effect of the flat portion does not result in an improvement in sound transmission loss from 315 Hz onwards. On the other hand, in Examples 1 and 2, not only is sound insulation performance improved by the increase in primary resonance frequency, but the proportion of flat portions is lower than in the Comparative Example, so sound insulation performance is improved over a wider range. [Explanation of symbols]

[0035] 1...Soundproof panel 2…Uneven structure 2A…first curved surface part 2B…Second curved surface part 3…Plane part

Claims

1. A sound-insulating panel having a concave-convex structure, The thickness T of the member constituting the concave-convex structure is 0.1 mm or more and 20 mm or less, The tensile modulus of the members constituting the concave-convex structure is 0.1 GPa or more, The length of a side of a square having the same area as the projected area of ​​the sound-insulating panel is defined as a side length L, and the product of the primary resonance frequency f [Hz] of the out-of-plane vibration of the sound-insulating panel and the side length L [m] is 80 [Hz m] or more, The height H from the lowest part to the highest part of the concave-convex structure the quotient of the side length L [m] and the side length L [m] is 0.01 or more and 0.7 or less, A sound-insulating panel in which the ratio of the projected area excluding the uneven structure to the entire projected area projected in the thickness direction is less than 20%.

2. The sound-insulating panel according to claim 1 , wherein the member constituting the uneven structure is made of metal or resin.

3. The sound-insulating panel according to claim 1 , wherein the uneven structure is singular.

4. The sound-insulating panel according to claim 1 , wherein the concave-convex structure has a plurality of curved surface portions with different curvatures.

5. The surface density of the members constituting the sound-insulating panel is 200 kg / m ３ 12,000kg / m or more ３ 2. The sound-insulating panel of claim 1, wherein:

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