Sound-shielding structure and sound-proof structure

Abstract

A sound-shielding structure (1) is provided with an elastic membrane section (2), an elastic support wall section (3) provided upright on the membrane section (2), and a weight section (4) provided upright on the membrane section (2). The membrane part (2) is divided into a plurality of partitions (5) by the support wall part (3), the counterweight parts (4) are respectively positioned inside all of the plurality of partitions (5) or inside some of the plurality of partitions (5), and one counterweight part (4) is arranged in one partition (5) in the partitions (5) in which the counterweight parts (4) are positioned. The height (H1) of the support wall section (3) extending in the direction orthogonal to the membrane section (2) is greater than the height (H2) of the weight section (4) extending in the direction orthogonal to the membrane section (2). Each of the weight parts (4) constitutes a spring mass resonator provided with an elastic spring part (4a) and a mass part (4b) having a larger mass than the spring part (4a). The sound-shielding structure (1) can obtain sufficient sound-shielding properties, can be easily and stably placed on a curved-surface-shaped placement surface, and is thin and lightweight. The sound-proof structure (11) comprises a sound-proof plate-shaped part (10) and a sound-proof structure part (9) composed of the sound-proof structure (1), at least one of the film part (2) and the support plate part (3) and the sound-proof plate-shaped part (10) are integrally formed or joined, and the sound-proof plate-shaped part (10) and the sound-proof structure part (9) are arranged side by side on a plane.

Description

Technical Field

[0001] The present invention relates to a sound insulation structure and a soundproof structure. Background Art

[0002] In recent years, in the indoor of buildings such as collective housing, office buildings, hotels, etc., it is required to block the outdoor noise from cars, rail trains, airplanes, ships, etc. outside the building, the equipment noise and human voice generated outside the room in the building, and the quietness suitable for the purpose of the room. In addition, in the interior of vehicles such as cars, rail trains, airplanes, ships, etc., in order to block wind noise and engine sound and provide passengers with a quiet and comfortable space, it is expected to reduce noise. Therefore, a means to block the propagation of noise or vibration from the outside to the inside of a building or a vehicle, or the propagation of noise or vibration from the outside to the inside of a building or a vehicle, that is, a component with high soundproofing properties is sought. In recent years, in buildings, with the increase in height, etc., lightweight soundproofing components are required. In addition, in vehicles, lightweight soundproofing components are also required to improve energy efficiency. Patent documents 1 to 6 disclose examples of soundproofing structures such as soundproofing walls formed in vehicles or buildings.

[0003] Patent Documents 1 and 2 disclose automotive dash mufflers (also called dash vibration isolating pads). These dash mufflers are stacked on a dash panel (instrument panel) located at the boundary between the engine compartment and the vehicle cabin to suppress the entry of noise from the engine compartment into the vehicle cabin. The dash mufflers have a single-layer structure or a multi-layer structure containing felt or polyurethane foam as a sound absorbing material.

[0004] In the invention described in Patent Document 3, in a sound attenuation panel having a rigid frame divided into a plurality of units, a thin plate of a flexible material, and a plurality of weights, each weight is fixed to the thin plate of the flexible material in such a manner that a weight is provided in each unit, and the attenuated sound is controlled by appropriately selecting the mass of the weight.

[0005] In the invention described in Patent Document 4, in a soundproofing member including an elastic thin plate and a support portion that holds the thin plate and divides the thin plate into partitions, the relationship between the rigidity of the thin plate in the partitions and the surface density of the thin plate is defined.

[0006] The sound-insulating material of the invention described in Patent Document 5 is a structure having a flat substrate portion and a plurality of resonance portions connected to the substrate portion and having a predetermined resonance frequency, wherein the plurality of resonance portions respectively have a weight portion and a connection portion connecting the weight portion and the substrate portion, and are constructed so that, in a projection viewed from a direction perpendicular to the substrate portion, the center of gravity of the resonance portion is located outside a joining region between the substrate portion and the connection portion.

[0007] The vibration reduction device of the invention described in Patent Document 6 has a sound element structure that is mounted on a vehicle body and blocks vibrations transmitted through the vehicle body, and includes: a cross-shaped frame that is mounted on the vehicle body and divides a constant space into constant areas; and a vibrator that is formed at the corners of each area divided by the frame and is constructed in a manner that has its own natural frequency and blocks vibrations transmitted from the vehicle body through the frame.

[0008] Prior art literature

[0009] Patent Literature

[0010] Patent Document 1: Japanese Patent Application Publication No. 2007-210381

[0011] Patent Document 2: Japanese Patent Application Publication No. 2018-012353

[0012] Patent Document 3: Japanese Patent Application Publication No. 2005-250474

[0013] Patent Document 4: International Publication No. WO2019 / 022245

[0014] Patent Document 5: Japanese Patent Application Publication No. 2021-152584

[0015] Patent Document 6: Japanese Patent Application Publication No. 2020-91481 Summary of the invention

[0016] Problems to be solved by the invention

[0017] The dash mufflers described in Patent Documents 1 and 2 cannot sufficiently reduce the noise entering the vehicle cabin. In particular, there is a problem that the road noise propagating from the bottom surface into the vehicle cabin is large, and a quiet and comfortable space cannot be provided for passengers.

[0018] The sound attenuation panel described in Patent Document 3 has a rigid frame that is not flexible, and vibration is transmitted to the thin plate via the rigid frame, so there is a problem that sufficient sound insulation cannot be obtained. In addition, when the mounting surface of the rigid frame has a curved surface or a concave-convex surface, there is a possibility that the sound attenuation panel cannot be stably maintained. In particular, there are many curved or concave-convex parts on the panels of ordinary vehicles (such as automobiles), so it is difficult to simply use the sound attenuation panel of Patent Document 3 as a sound insulation material for vehicles. In addition, sometimes the mass of the rigid frame is large, and the increase in mass caused by the sound insulation material in the vehicle becomes a problem.

[0019] The height of the support portion of the soundproofing member described in Patent Document 4, i.e., the height extending from the thin plate in a direction perpendicular to the thin plate, is high, preferably above 25 mm. Therefore, in order to stably support the thin plate by means of a high support portion, the support portion is preferably rigid. As a result, vibration is transmitted via the support portion, so there is a problem of insufficient sound insulation, and it is difficult to place the soundproofing member on a curved or concave-convex placement surface such as a panel of a vehicle (e.g., a car). In addition, the high support portion causes the overall size and weight of the soundproofing member to increase. When placed on a panel of a vehicle, there is the following problem: the soundproofing member occupies a large space inside the vehicle, which reduces the space efficiency, hinders the installation of other components, or hinders the passengers.

[0020] In the sound insulation material described in Patent Document 5, the functional part that exerts the sound insulation effect, namely the resonance part, is exposed and not covered by the supporting wall, etc. If other parts or the human body touch the resonance part, the sound insulation performance may be reduced or changed. Therefore, a larger space needs to be provided around the resonance part, which reduces the space efficiency.

[0021] The vibration reduction device described in Patent Document 6 does not have a membrane portion, but is composed of a plurality of vibrators and a frame connecting them. Therefore, similar to the sound insulation material of Patent Document 5, the functional portion that exerts the sound insulation effect, namely the vibrator, is exposed, and if other parts or the human body touch the vibrator, the sound insulation may be reduced or changed. In addition, in order to ensure the minimum structural strength of the vibration reduction device, the frame is required to have rigidity. As a result, the vibration is transmitted through the frame, so that sufficient sound insulation may not be obtained, and it is difficult to place the vibration reduction device of Patent Document 6 on a curved or concave-convex mounting surface such as a panel of a passenger vehicle (such as a car).

[0022] Therefore, an object of the present invention is to provide a sound insulating structure and a soundproof structure including the sound insulating structure, wherein the sound insulating structure is thin and lightweight, can obtain sufficient sound insulating properties, and can be easily and stably placed on a curved or concave-convex mounting surface such as a panel of a building, a mechanical device, or a vehicle (such as a car), and has good sound insulating properties particularly in the low-frequency region below 1000 Hz.

[0023] Solutions to Solve Problems

[0024] The first sound insulation structure of the present invention is characterized in that it comprises: an elastic diaphragm portion; an elastic supporting wall portion erected on the diaphragm portion; and a counterweight portion erected on the diaphragm portion, the diaphragm portion being divided into a plurality of zones by the supporting wall portion, the counterweight portions being located inside all of the plurality of zones or inside a portion of the plurality of zones, respectively, and in the zones where the counterweight portions are located, one counterweight portion is arranged in one of the zones, the height of the supporting wall portion extending in a direction perpendicular to the diaphragm portion is greater than the height of the counterweight portion extending in a direction perpendicular to the diaphragm portion, and the counterweight portions respectively constitute spring mass resonators having an elastic spring portion and a mass portion having a mass greater than that of the spring portion.

[0025] In addition, elasticity as used herein refers to the property of a solid material that is deformed by a force applied from the outside and returns to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, a case where at least one of energy elasticity and rubber elasticity (entropy elasticity) is present is referred to as "having elasticity".

[0026] The supporting wall portion and the spring portion may be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane portion may be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0027] The membrane portion, the support wall portion, and the spring portion may all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz. In addition, the membrane portion, the support wall portion, and the spring portion may all be formed of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz.

[0028] Specifically, the elasticity of the membrane portion, the supporting wall portion, and the spring portion is evaluated by the dynamic storage modulus (E'), which is obtained by measuring the frequency dependence in the tension or compression mode of the dynamic viscoelasticity measuring device based on JIS K7244 and obtaining the master curve of the 23°C reference, and the dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is 0.01MPa or more and 100MPa or less. Further, it is more preferred that the above-mentioned membrane portion and the above-mentioned supporting wall portion can be composed of an elastomer having a dynamic storage modulus (E') of 0.05MPa or more and 50MPa or less at 23°C and a frequency of 1Hz to 1000Hz, and a loss tangent of 0.05 or more and 0.45 or less at 23°C and a frequency of 1Hz to 1000Hz.

[0029] The spring portion of the weight portion may be located at a side where the weight portion is mounted on the diaphragm portion, and the mass portion may be located at a side opposite to a side where the weight portion is mounted on the diaphragm portion.

[0030] The volume of the mass portion of the weight portion may be larger than the volume of the spring portion.

[0031] The mass portion of the weight portion may be formed of a material having a density greater than that of the spring portion.

[0032] The second sound insulation structure of the present invention is characterized in that it comprises: an elastic diaphragm portion; an elastic supporting wall portion erected on the diaphragm portion; and a counterweight portion erected on the diaphragm portion, the diaphragm portion is divided into a plurality of zones by the supporting wall portion, the counterweight portion is respectively located inside all of the plurality of zones or inside a portion of the plurality of zones, and in the zones where the counterweight portion is located, one counterweight portion is arranged in one of the zones, the height of the supporting wall portion extending in a direction perpendicular to the diaphragm portion is greater than the height of the counterweight portion extending in a direction perpendicular to the diaphragm portion, the diaphragm portion serves as a spring portion and the counterweight portion serves as a mass portion to form a spring mass resonator.

[0033] The supporting wall portion may be made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane portion may be made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0034] The dynamic storage modulus of the membrane portion and the supporting wall portion at 23°C and a frequency of 1Hz to 1000Hz may be 0.01MPa or more and 100MPa or less. In addition, the membrane portion and the supporting wall portion may be composed of an elastomer whose loss tangent at 23°C and a frequency of 1Hz to 1000Hz is 0.01 or more and 0.50 or less. More preferably, the membrane portion and the supporting wall portion may be composed of an elastomer whose dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is 0.05MPa or more and 50MPa or less, and whose loss tangent at 23°C and a frequency of 1Hz to 1000Hz is 0.05 or more and 0.45 or less.

[0035] The supporting wall portion may include: a plurality of first wall portions extending in a direction perpendicular to the membrane portion and in a first direction parallel to the membrane portion; and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and in a second direction perpendicular to the first direction.

[0036] The area of ​​each of the above-mentioned zones can be 100mm 2 Above and 1000mm 2 the following.

[0037] Each 1000cm of the above membrane 2 The number of the above-mentioned sections can be 10 or more and 1000 or less, and preferably 50 or more and 500 or less.

[0038] The supporting wall portion may be a cylindrical shape having a circular, elliptical or oblong cross-sectional shape dividing each of the above-mentioned areas, or a square cylindrical shape having a polygonal cross-sectional shape dividing each of the above-mentioned areas, specifically a square, regular pentagon or regular hexagonal cross-sectional shape.

[0039] The support wall portion may have a thickness of 0.5 mm to 5.0 mm, preferably 1.0 mm to 3.0 mm.

[0040] The film thickness of the film portion may be greater than or equal to 0.1 mm and less than or equal to 3.0 mm.

[0041] The height perpendicular to the membrane portion may be 5 mm or more and 20 mm or less.

[0042] The height of the support wall portion extending in a direction perpendicular to the membrane portion may be 5 mm to 20 mm, preferably 10 mm to 20 mm. The support wall portion may have a partially different height.

[0043] There may be a plurality of the above-mentioned supporting wall portions, and the height of a part of the above-mentioned supporting wall portions extending in a direction orthogonal to the above-mentioned membrane portion is higher than the height of the other above-mentioned supporting wall portions. Moreover, the height of the above-mentioned supporting wall portions with a higher height extending in a direction orthogonal to the above-mentioned membrane portion may be greater than 10 mm and less than 20 mm, and the height of the other above-mentioned supporting wall portions (the above-mentioned supporting wall portions with a lower height) may be less than 10 mm. In addition, the supporting wall portions with a higher height mentioned here refer to supporting wall portions with a height higher (for example, more than 1 mm) than other supporting wall portions (supporting wall portions with a lower height).

[0044] The height of the weight portion extending in a direction perpendicular to the membrane portion may be 1 mm or more.

[0045] The durometer A hardness of the film portion may be 30 or more, and the durometer A hardness of the support wall portion may be 1 or more and 90 or less. The durometer A hardness can be obtained by measuring in accordance with JIS K6253-3.

[0046] The first soundproof structure of the present invention is composed of a soundproof plate-like portion and a soundproofing structure portion, and is characterized in that the soundproof plate-like portion is a plate-like component made of a sound-absorbing material or a soundproofing material, the soundproofing structure portion is composed of the first soundproofing structure, at least one of the membrane portion and the support plate portion is formed as a whole with the soundproof plate-like portion, or is joined to each other, and the soundproof plate-like portion and the soundproofing structure portion are arranged in a plane. The first soundproof structure may have the following structure.

[0047] The membrane portion, the support wall portion, and the spring portion may be made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0048] The membrane portion, the support wall portion, and the spring portion may all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz. In addition, the membrane portion, the support wall portion, and the spring portion may all have a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz.

[0049] Specifically, the elasticity of the membrane, the supporting wall and the spring is evaluated by the dynamic storage modulus (E'), which is obtained by measuring the frequency dependence in the tension or compression mode of the dynamic viscoelasticity measuring device based on JIS K7244 and obtaining the master curve of the 23°C reference, and the dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is 0.01MPa or more and 100MPa or less. Further, it is more preferred that the dynamic storage modulus (E') of the membrane and the supporting wall at 23°C and a frequency of 1Hz to 1000Hz is 0.05MPa or more and 50MPa or less, and the loss tangent at 23°C and a frequency of 1Hz to 1000Hz is 0.05 or more and 0.45 or less.

[0050] The spring portion may be located at a side where the weight portion is mounted on the diaphragm portion, and the mass portion may be located at a side opposite to a side where the weight portion is mounted on the diaphragm portion.

[0051] The mass portion may have a volume greater than a volume of the spring portion.

[0052] The mass portion may be formed of a material having a density greater than that of the spring portion.

[0053] The second soundproof structure of the present invention is composed of a soundproof plate-like part and a soundproofing structure part, and is characterized in that the soundproof plate-like part is a plate-like component made of a sound absorbing material or a soundproofing material, the soundproofing structure part is composed of the second soundproofing structure, at least one of the membrane part and the support plate part is formed as a whole with the soundproof plate-like part, or is joined to each other, and the soundproof plate-like part and the soundproofing structure part are arranged in a plane. The second soundproof structure can have the following structure.

[0054] The membrane portion and the support wall portion may be each made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0055] The above-mentioned membrane portion and the above-mentioned supporting wall portion may have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz. In addition, the above-mentioned membrane portion and the above-mentioned supporting wall portion may have a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More preferably, the above-mentioned membrane portion and the above-mentioned supporting wall portion may have a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent of 0.05 or more and 0.45 or less at 23°C and a frequency of 1 Hz to 1000 Hz.

[0056] The area occupied by the soundproofing structure on the main surface of the soundproofing structure is not less than 5% and not more than 95% of the area of ​​the entire soundproofing structure.

[0057] The first soundproofing structure and the second soundproofing structure may have the following structures.

[0058] The supporting wall portion may include: a plurality of first wall portions extending in a direction perpendicular to the membrane portion and in a first direction parallel to the membrane portion; and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and in a second direction perpendicular to the first direction.

[0059] The supporting wall portion may be a cylindrical shape having a circular, elliptical or oblong cross-sectional shape dividing each of the above-mentioned areas, or a square cylindrical shape having a polygonal cross-sectional shape dividing each of the above-mentioned areas, specifically a square, regular pentagon or regular hexagonal cross-sectional shape.

[0060] The area of ​​each of the above-mentioned zones can be 100mm 2 Above and 1000mm 2 the following.

[0061] Each 1000cm of the above membrane 2 The area may be provided with 10 or more and 1000 or less of the above-mentioned partitions. More preferably, the above-mentioned membrane portion has an area of ​​1000 cm 2 The area may be provided with 50 or more and 500 or less of the above-mentioned sections.

[0062] The thickness of the support wall portion may be 0.5 mm to 5.0 mm. More preferably, the thickness of the support wall portion may be 1.0 mm to 3.0 mm. In addition, the thickness of the membrane portion may be 0.1 mm to 3.0 mm.

[0063] The height perpendicular to the membrane portion may be 5 mm or more and 20 mm or less.

[0064] The height of the support wall portion extending in a direction perpendicular to the membrane portion may be 5 mm to 20 mm, and the height may be partially different.

[0065] The height of the weight portion extending in a direction perpendicular to the membrane portion may be 1 mm or more.

[0066] The durometer A hardness of the film portion may be 30 or more, and the durometer A hardness of the support wall portion may be 1 or more and 90 or less. The durometer A hardness can be obtained by measuring in accordance with JIS K6253-3.

[0067] At least one of the membrane portion and the support plate portion and the soundproof plate-like portion may be formed as one piece by insert molding, or may be joined to each other by any one of ultrasonic welding, bonding by adhesive, and fixing by clips, bolts, and rivets. In addition, the soundproofing structure portion and the soundproofing plate-like portion may be joined to each other by improving the shape of the soundproofing plate-like portion or the soundproofing structure portion. For example, the soundproofing plate-like portion may be provided with an embedding hole, and the soundproofing plate-like portion may be joined only by embedding a portion of the membrane portion into the embedding hole.

[0068] The soundproof plate-like portion may have a single-layer structure including any one of a layer made of felt, polyurethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are stacked.

[0069] The sound insulation structure can be installed on a panel inside a car. Furthermore, the sound insulation structure can be installed on a dash panel of a car, and the sound insulation structure can be installed on a position facing a tire.

[0070] Effects of the Invention

[0071] According to the present invention, a sound insulating structure and a soundproofing structure including the sound insulating structure can be provided. The sound insulating structure is thin and lightweight, can obtain sufficient sound insulating properties, can be easily and stably placed on a curved or concave-convex placing surface such as a panel of a building, a mechanical device, or a passenger vehicle (such as a car), and has good sound insulating properties particularly in the low-frequency region below 1000 Hz. BRIEF DESCRIPTION OF THE DRAWINGS

[0072] Figure 1A It is a perspective view of the sound insulating structure according to the first embodiment of the present invention.

[0073] Figure 1B yes Figure 1A A-A line cross-sectional view.

[0074] Figure 2A yes Figure 1A , 1B An exploded perspective view of a section of the sound insulation structure shown.

[0075] Figure 2B yes Figure 1A , 1B An exploded front view of a section of the sound insulation structure is shown.

[0076] Figure 3A It is a perspective view of a sound insulating structure according to a modified example of the first embodiment of the present invention.

[0077] Figure 3B yes Figure 3A A-A line cross-sectional view.

[0078] Figure 4A It is a cross-sectional view of a sound insulating structure according to another modified example of the first embodiment of the present invention.

[0079] Figure 4B yes Figure 4A A three-dimensional view of the weight portion of the sound insulation structure shown.

[0080] Figure 5A It is a cross-sectional view of a sound insulating structure according to still another modified example of the first embodiment of the present invention.

[0081] Figure 5B yes Figure 5A A three-dimensional view of the weight portion of the sound insulation structure shown.

[0082] Fig. 6A It is a perspective view of a sound insulating structure according to a second embodiment of the present invention.

[0083] Figure 6B yes Fig. 6A A-A line cross-sectional view.

[0084] Fig. 7A It is a cross-sectional view of a sound insulating structure according to a modified example of the second embodiment of the present invention.

[0085] Figure 7B yes Fig. 7A A three-dimensional view of the weight portion of the sound insulation structure shown.

[0086] Fig. 8A It is a top view schematically showing one section of the sound insulating structure of the present invention.

[0087] Figure 8B It is a plan view schematically showing a plurality of partitions of the sound insulating structure of the present invention.

[0088] Fig. 9A This is a plan view schematically showing one section of another example of the sound insulating structure of the present invention.

[0089] Fig. 9B It is a plan view schematically showing a plurality of partitions of another example of the sound insulating structure of the present invention.

[0090] Fig. 10A This is a plan view schematically showing one section of still another example of the sound insulating structure of the present invention.

[0091] Fig. 10B It is a plan view schematically showing a plurality of partitions of still another example of the sound insulating structure of the present invention.

[0092] Fig.11A This is a plan view schematically showing one section of still another example of the sound insulating structure of the present invention.

[0093] Fig. 11B It is a plan view schematically showing a plurality of partitions of still another example of the sound insulating structure of the present invention.

[0094] Fig. 12A This is a plan view schematically showing one section of still another example of the sound insulating structure of the present invention.

[0095] Fig. 12B It is a plan view schematically showing a plurality of partitions of still another example of the sound insulating structure of the present invention.

[0096] Fig.13 It is a cross-sectional view showing a state where the sound insulating structure according to Example 1 of the present invention is attached to an iron plate.

[0097] Fig.14A It is a graph showing the sound insulating properties of Example 1 of the present invention and Comparative Examples 1 to 3.

[0098] Fig. 14B It is a graph showing the sound insulating properties of Examples 1 to 3 of the present invention and Comparative Example 3.

[0099] Fig. 14C It is a graph showing the sound insulating properties of Examples 1 and 4 of the present invention and Comparative Example 4.

[0100] Fig.14D It is a graph showing the sound insulating properties of Examples 1 and 5 of the present invention.

[0101] Fig.14E It is a graph showing the sound insulating properties of Examples 1 and 6 of the present invention.

[0102] Fig.14F It is a graph showing the sound insulating properties of Examples 1, 7, 8 and Comparative Example 3 of the present invention.

[0103] Figure 14G It is a graph showing the sound insulation performance of Examples 8 and 9 of the present invention.

[0104] Fig.14H It is a graph showing the sound insulation performance of Examples 9 and 10 of the present invention.

[0105] Fig.14I It is a graph showing the sound insulating properties of Examples 9 and 11 of the present invention.

[0106] Fig.14J It is a graph showing the sound insulating properties of Examples 12 to 14 of the present invention and Comparative Example 5.

[0107] Figure 14K It is a graph showing the sound insulating properties of Example 1 and Comparative Example 6 of the present invention.

[0108] Fig.15 This is a cross-sectional view of the structure of Comparative Example 1.

[0109] Fig.16A It is a perspective view of the sound insulation structure of Comparative Example 3.

[0110] Fig. 16B Yes means Fig.16A The sound insulation structure shown is a cross-sectional view of a state in which it is attached to an iron plate.

[0111] Fig.17 It is a cross-sectional view showing a state where a sound insulating structure according to Example 2 of the present invention is attached to an iron plate.

[0112] Fig.18A It is a perspective view of a sound insulation structure according to Example 3 of the present invention.

[0113] Fig.18B Yes means Fig.18A The sound insulation structure shown is a cross-sectional view of a state in which it is attached to an iron plate.

[0114] Fig.19A It is a stereoscopic view of a sound insulation structure according to Example 6 of the present invention.

[0115] Fig.19B Yes means Fig.19A The sound insulation structure shown is a cross-sectional view of a state in which it is attached to an iron plate.

[0116] Fig. 20 It is a cross-sectional view showing a state where the sound insulating structure according to Example 10 of the present invention is attached to an iron plate.

[0117] Fig.21A It is a stereoscopic view of a sound insulation structure according to Example 11 of the present invention.

[0118] Fig. 21B Yes means Fig.21A The sound insulation structure shown is a cross-sectional view of a state in which it is attached to an iron plate.

[0119] Fig. 22 It is a side view of a car which is an example of a passenger vehicle provided with the soundproofing structure of the present invention.

[0120] Fig.23 yes Fig. 22 A side view of the soundproofing structure is shown.

[0121] Fig.24 yes Fig. 22 The soundproofing structure shown is a perspective view seen from the front side.

[0122] Fig.25 yes Fig.24 C-C line cross-sectional view. DETAILED DESCRIPTION

[0123] Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0124] [First embodiment]

[0125] Figure 1A 1 is a perspective view of a sound insulation structure 1 according to a first embodiment of the present invention. Figure 1B is Figure 1A A cross-sectional view after cutting at the A-A line and turning it upside down. The sound insulation structure 1 has: a thin plate-shaped diaphragm portion 2 having elasticity; a supporting wall portion 3 having elasticity and being erected substantially vertically from the diaphragm portion 2; and a counterweight portion 4 having been erected substantially vertically from the diaphragm portion 2. The diaphragm portion 2 is divided into a plurality of partitions (unit structures) 5 by the supporting wall portion 3. Counterweight portions 4 are respectively provided inside all of the plurality of partitions 5 or inside a portion of the plurality of partitions 5. Among the partitions 5 having counterweight portions 4 provided therein, a counterweight portion 4 is provided in one of the partitions 5. Figure 2A is an exploded perspective view of a partition 5 of the sound insulation structure 1. Figure 2B It is its exploded front view. The height H1 of the support wall portion 3 extending from the membrane portion 2 in a direction perpendicular to the membrane portion 2 is greater than the height H2 of the counterweight portion 4 extending from the membrane portion 2 in a direction perpendicular to the membrane portion 2. The counterweight portion 4 is respectively provided with a spring portion 4a having elasticity and a mass portion (mass block portion) 4b having a mass greater than the mass of the spring portion 4a, thereby forming a spring mass resonator. The so-called elasticity here refers to the property of a solid material that is deformed by a force applied from the outside and returns to its original shape when the external force is removed, including energy elasticity and rubber elasticity (entropy elasticity). Here, the situation of having at least one of energy elasticity and rubber elasticity (entropy elasticity) is referred to as "having elasticity".

[0126] The support wall portion 3 of the present embodiment includes a plurality of first wall portions 3a extending along a first direction D1 parallel to the membrane portion 2 and a plurality of second wall portions 3b extending along a second direction D2 orthogonal to the first direction D1. Specifically, a plurality of first wall portions 3a are arranged in parallel, and a plurality of second wall portions 3b are arranged in parallel, and the first wall portion 3a and the second wall portion 3b are integrated at the intersection. In this way, a plurality of first wall portions 3a and a plurality of second wall portions 3b constitute a lattice structure, and a plurality of partitions 5 having a square plane shape separated by the first wall portion 3a and the second wall portion 3b are arranged in a matrix. In other words, the support wall portion 3 is a structure in which a plurality of square tubes are arranged, and the square tube has a square cross-sectional shape that divides each partition 5. The support wall portion 3 is preferably composed of soft materials such as rubber, elastomer, and resin foam. The soft material mentioned here is any one of a material having rubber elasticity without energy elasticity, a material having energy elasticity without rubber elasticity, and a material having both rubber elasticity and energy elasticity.

[0127] The portion of the weight portion 4 of this embodiment mounted on one side of the diaphragm portion 2 is the spring portion 4a, and the portion mounted on the opposite side of the diaphragm portion 2 is the mass portion 4b having a greater mass than the spring portion 4a. Figures 1A to 2B In the example shown, the spring portion 4a and the mass portion 4b have the same shape and the same size, but are made of different materials. The spring portion 4a is made of a soft material, and the mass portion 4b is made of a material having a density greater than that of the material constituting the spring portion 4a. The spring portion 4a functions as a spring, and the mass portion 4b functions as a mass block, constituting a spring mass resonator. In addition, sometimes the membrane portion 2 also functions as a part of the spring of the spring mass resonator together with the spring portion 4a of the counterweight portion 4. Furthermore, the air in the space surrounded by the membrane portion 2 and the supporting wall portion 3 also functions as a part of the spring of the spring mass resonator (air spring). The spring portion 4 is also preferably made of any one of a soft material, that is, a material having rubber elasticity without energy elasticity, a material having energy elasticity without rubber elasticity, and a material having both rubber elasticity and energy elasticity.

[0128] According to the sound insulation structure 1 of the present embodiment, the vibration of the diaphragm portion 2 is controlled by the action of the spring mass resonator composed of the spring portion 4a and the mass portion 4b of the weight portion 4. In particular, in a specific frequency range (for example, the main frequency band of road noise of automobiles, that is, frequencies below 1000 Hz), the vibration of the diaphragm portion 2 is greatly reduced, and as a result, the radiated sound from the diaphragm portion 2 is reduced, thereby achieving high sound insulation.

[0129] The partitions 5 of the sound insulating structure 1 of the present embodiment are preferably arranged at a distance of 1000 cm from the diaphragm 2. 2 The area is set to be more than 10 and less than 1000, and more preferably more than 50 and less than 500. If, for example, there are too few zones 5, the effect of dividing the entire sound insulation structure 1 into a plurality of zones 5 and making each zone reflect the sound insulation effect is insufficient, and there is a problem of reduced sound insulation of the entire sound insulation structure 1. On the other hand, if there are too many zones 5, there is a problem of increased weight of the entire sound insulation structure 1. The area of ​​the plane shape of each zone 5 is preferably 100 mm 2 Above and 1000mm 2 Below, more preferably 200mm 2 Above and 800mm 2Below. If the area of ​​the planar shape of each partition 5 is too small, there is a problem that it is difficult to arrange the counterweight part 4 inside. On the other hand, if the area is too large, the effect of the counterweight part 4 relative to the membrane part 2 is insufficient, and there is a problem of reduced sound insulation. The height of the overall sound insulation structure 1 in a direction perpendicular to the membrane part 2 is preferably greater than 5 mm and less than 20 mm. If the height of the overall sound insulation structure 1 is too low, there is a problem that the counterweight part 4 cannot have a sufficient height as a spring mass resonator. On the other hand, if it is too high, there is a problem that the weight of the overall sound insulation structure 1 increases. In addition, each drawing schematically illustrates each partition 5 and the supporting wall part 3, etc. The number and area of ​​the partitions 5 or the height of the sound insulation structure 1 are sometimes not strictly and correctly illustrated, and sometimes are not unified in each drawing, but it is preferred that the number and area of ​​the partitions 5 and the height of the sound insulation structure 1 are appropriately designed to be within the above-mentioned numerical ranges.

[0130] The membrane portion 2, the supporting wall portion 3 and the spring portion 4a of the sound insulation structure 1 of the present embodiment are all composed of an elastomer, and the dynamic storage modulus (E') of the elastomer at 23°C and a frequency of 1Hz to 1000Hz is 0.01MPa or more and 100MPa or less, and the loss tangent (tanδ) at 23°C and a frequency of 1Hz to 1000Hz is 0.01 or more and 0.50 or less, preferably the dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is 0.05MPa or more and 50MPa or less, and the loss tangent (tanδ) at 23°C and a frequency of 1Hz to 1000Hz is 0.05 or more and 0.50 or less. The dynamic storage modulus (E') and the loss tangent (tanδ) are obtained by making a master curve based on 23°C using a dynamic viscoelasticity tester. Assume that if the dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is less than 0.01MPa, there is a problem that the sound insulation of the target frequency band deteriorates, and there is a problem that the shape retention of the membrane 2 or the supporting wall 3 also deteriorates. If the dynamic storage modulus (E') at 23°C and a frequency of 1Hz to 1000Hz is greater than 100MPa, there is a problem that the vibration of the frequency band that becomes the sound insulation target deteriorates, the sound insulation structure 1 becomes rigid, and there is a problem that the installation property also deteriorates. The membrane 2 and the supporting wall 3 can be formed of the same material or different materials. The membrane 2 is also preferably composed of any one of a soft material, that is, a material that does not have energy elasticity but has rubber elasticity, a material that does not have rubber elasticity but has energy elasticity, and a material that has both rubber elasticity and energy elasticity.

[0131] The diaphragm 2 is preferably a hard elastic membrane because it is installed for the counterweight part 4. The dynamic storage modulus (E') of the diaphragm 2 is preferably greater than 15 MPa, and the thickness (film thickness) is preferably greater than 0.1 mm and less than 3.0 mm, and more preferably about 0.5 mm. Assuming that if the thickness of the diaphragm 2 is less than 0.1 mm, the vibration of the diaphragm 2 will be deteriorated, and there will be a problem that the sound insulation of the frequency band that is the object of sound insulation will be deteriorated. If the thickness of the diaphragm 2 is greater than 3.0 mm, there will be a problem that the thickness and weight of the entire sound insulation structure 1 increase. The material of the diaphragm 2 is preferably greater than 30 in the durometer A hardness obtained based on JIS K6253, and more preferably greater than 70. If the durometer A hardness of the diaphragm 2 is less than 30, the vibration of the diaphragm 2 will be deteriorated, and there will be a problem that the sound insulation of the frequency band that is the object of sound insulation will be deteriorated. The rigidity (axial rigidity) k of the membrane 2 is expressed as k=E'×A / L from the dynamic storage modulus E', the cross-sectional area A of the membrane 2, and the thickness L of the membrane 2. When the area of ​​the membrane 2 to be evaluated for rigidity is 1000 cm 2 When the rigidity k is preferably 10 6 N / mm or more and 10 9 N / mm or less, more preferably 3×10 6 N / mm or more and 10 8 N / mm or less. If the area of ​​the membrane part 2 is 1000cm 2 When the rigidity is less than 10 6 N / mm, the vibration of the diaphragm 2 deteriorates, and there is a problem that the sound insulation performance in the frequency band to be soundproofed deteriorates. 2 The rigidity ratio is 10 9 If the N / mm is large, the sound insulation structure 1 becomes rigid and the installation property becomes poor. In addition, the bending rigidity K of the membrane 2 is expressed by the dynamic storage modulus E' and the secondary moment of area I as K = E' × I, and the secondary moment of area I is calculated by the thickness h of the membrane 2 and the width b of the membrane 2 as I = b × h 3 / 12. The area of ​​the membrane portion 2 to be evaluated is 1000 cm 2 When the bending rigidity K is preferably 30N / mm 2 Above and 10 5 N / mm 2 Below, more preferably 50N / mm 2 Above and 5×10 4 N / mm 2 If the area of ​​the membrane portion 2 is 1000cm 2 The bending rigidity K is less than 30N / mm 2 , the vibration of the membrane 2 deteriorates, and there is a problem that the sound insulation performance of the frequency band to be soundproofed deteriorates. If the area of ​​the membrane 2 is 1000cm 2 The bending rigidity K is 105 N / mm 2 If the diameter is large, the sound insulating structure 1 becomes rigid and the installation property is deteriorated. The cross-sectional shape of the membrane 2 is not particularly limited and may be flat or concave-convex.

[0132] As the material of the membrane portion 2, cross-linked (vulcanized) rubber, thermoplastic elastomer, and plastic can be cited. As the cross-linked (vulcanized) rubber, for example, natural rubber (NR), isoprene rubber (IR), butadiene rubber (BR), ethylene-butadiene rubber (SBR), chloroprene rubber (CR), butyl rubber (IIR), nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), ethylene-propylene rubber (EPM), ethylene-propylene-diene rubber (EPDM), and ethylene-butene-diene rubber (EBDM) and other ethylene-α-olefin-non-conjugated polyene copolymers, chlorosulfonated polyethylene (CSM), chlorinated polyethylene (CM), acrylic rubber (ACM), ethylene-acrylic rubber (AEM), ethylene-vinyl acetate rubber (EVA), epichlorohydrin rubber (CO, ECO), polysulfide rubber (T), methyl vinyl silicone rubber (VMQ) and fluorinated silicone rubber (FVMQ) and other silicone rubber (Q), polyurethane rubber (U), fluororubber (FKM) and other materials obtained by cross-linking (vulcanizing) various rubber materials. These crosslinked (sulfurized) rubbers can be used alone or in combination of two or more. In addition, as a crosslinked (sulfurized) method, for example, organic peroxides, phenolic resins, oxime compounds, sulfur, sulfur-based compounds, and polyamine compounds can be cited as crosslinking agents (sulfurizing agents), and the method of crosslinking (sulfurizing) by heating or irradiating electron beams for crosslinking. In addition, various known compounding agents (carbon black, reinforcing agents such as silicon dioxide, fillers such as calcium carbonate, paraffin oil, softeners such as plasticizers, processing aids, antioxidants, light stabilizers, flame retardants, mildew inhibitors, acid binding agents, silane coupling agents, antistatic agents, ultraviolet light absorbers, etc.) that are usually used as rubber compounding agents can also be added to the crosslinked (sulfurized) rubber. These crosslinked (sulfurized) rubbers, crosslinking agents (sulfurizing agents), and compounding agents can also be composed of biomass raw materials.

[0133] Examples of thermoplastic elastomers include olefin-based thermoplastic elastomers, styrene-based thermoplastic elastomers, polyester-based thermoplastic elastomers, polyvinyl chloride-based thermoplastic elastomers, and ethylene-vinyl acetate-based thermoplastic elastomers. In addition, examples of plastics include polyethylene, polypropylene, polystyrene, polyethylene terephthalate, polyvinyl chloride, or composite resins containing these. These thermoplastic elastomers and plastics may also be made of biomass raw materials.

[0134] Specifically, the material of the membrane portion 2 is preferably ethylene-propylene-diene rubber, thermoplastic olefin elastomer, thermoplastic styrene elastomer, polyethylene, polypropylene, polyethylene terephthalate, thermoplastic polyurethane, or the like.

[0135] The supporting wall portion 3 is preferably made of a flexible soft material within the range that can support the membrane portion 2. The thickness of the supporting wall portion 3 is preferably 0.5 mm or more and 5.0 mm or less, and more preferably 1.0 mm or more and 3.0 mm or less. Assuming that the thickness of the supporting wall portion 3 is less than 0.5 mm, there is a problem that the shape retention of the sound insulation structure 1 is deteriorated. If the thickness of the supporting wall portion 3 is greater than 5.0 mm, the vibration of the membrane portion 2 is deteriorated, there is a problem that the sound insulation of the frequency band that becomes the sound insulation object is deteriorated, and there is a problem that the weight of the sound insulation structure 1 as a whole is also increased. The height of the supporting wall portion 3 extending in a direction orthogonal to the membrane portion 2 is preferably 5 mm or more and 20 mm or less, and more preferably 10 mm or more and 20 mm or less. The supporting wall portion 3 may also have a locally different height. In the case where the height of the supporting wall portion 3 is locally different, the portion with a higher height may be 10 mm or more and 20 mm or less, more preferably 12 mm or more and 20 mm or less, and further preferably 14 mm or more and 20 mm or less. If the height of the supporting wall portion 3 is too low, there is a problem that the counterweight portion 4 cannot have a sufficient height as a spring mass resonator. If the height of the supporting wall portion 3 is too high, there is a problem of an overall increase in weight. The material of the supporting wall portion 3 preferably has a durometer A hardness of 1 or more and 90 or less based on JIS K6253, and more preferably 10 or more and 70 or less. If the durometer A hardness of the supporting wall portion 3 is less than 1, there is a problem that the shape retention of the sound insulation structure 1 deteriorates. If the durometer A hardness of the supporting wall portion 3 is greater than 90, there are the following problems: the vibration from the supporting wall portion 3 is transmitted to the membrane portion 2, the sound insulation performance deteriorates, and the sound insulation structure 1 becomes rigid and the installation property deteriorates. Moreover, the rigidity k of the supporting wall portion 3 is expressed by the dynamic storage modulus E', the cross-sectional area A of the supporting wall portion 3, and the height L of the supporting wall portion 3 as k=E'×A / L. When the area of ​​the supporting wall portion 3 that is the object of rigidity evaluation is 1000cm 2 When the rigidity k is preferably 10 N / mm or more and 10 6 N / mm or less, more preferably 10 2 N / mm or more and 10 5 N / mm or less. If the area of ​​the supporting wall 3 is 1000cm 2 When the rigidity k is less than 10 N / mm, there is a problem that the shape retention of the sound insulation structure 1 is deteriorated. 2 The rigidity k is 10 6If N / mm is large, there are problems that the vibration from the supporting wall portion 3 is transmitted to the membrane portion 2, the sound insulation performance is deteriorated, and the sound insulation structure 1 becomes rigid and the installation property is deteriorated.

[0136] As the material of the supporting wall portion 3, crosslinked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. can be listed. Crosslinked (vulcanized) rubber, thermoplastic elastomer can be the same as the material listed as the material of the membrane portion 2. As the resin foam, it can be an independent bubble structure or a continuous bubble structure, and polyurethane foam, polystyrene foam, polyethylene foam, ethylene-vinyl acetate rubber (EVA) foam, etc. can be listed. Specifically, the material of the supporting wall portion 3 is preferably ethylene-propylene-diene rubber, polyurethane rubber, silicone rubber, thermoplastic olefin elastomer, thermoplastic styrene elastomer, thermoplastic polyurethane, polyurethane foam, etc. These resin foams can also be composed of biomass raw materials.

[0137] The material of the spring portion 4a of the weight portion 4 is a soft material such as cross-linked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. The cross-linked (vulcanized) rubber, thermoplastic elastomer, and resin foam can be the same as the material listed as the material of the support wall portion 3. Specifically, the material of the spring portion 4a of the weight portion 4 is preferably ethylene-propylene-diene rubber, polyurethane rubber, silicone rubber, thermoplastic olefin elastomer, thermoplastic styrene elastomer, thermoplastic polyurethane, polyurethane foam, etc.

[0138] The material of the mass portion 4b is not particularly limited, but is composed of resin or metal, etc. The mass of the mass portion 4b is greater than the mass of the spring portion 4a, and has a mass of, for example, more than 0.1g and less than 2.0g. The mass portion 4b preferably has a mass more than twice the mass of the spring portion 4a. Assuming that the weight of the mass portion 4b is less than twice the mass of the spring portion 4a, the counterweight portion 4 cannot fully resonate in the frequency region that becomes the sound insulation object, and there is a problem of poor sound insulation. In the case where the material of the mass portion 4b is a resin, the resin can also be composed of biomass raw materials.

[0139] The spring constant (rigidity) of the spring portion 4a is determined based on the mass of the mass portion 4b so that the resonant frequency coincides with the frequency of the main sound insulation target. For example, when the mass of the mass portion 4b is 1.0g and the frequency of the main sound insulation target is below 1000Hz, the spring constant of the spring portion 4a is above 1N / mm and below 50N / mm.

[0140] According to such a structure, the membrane portion 2, the support wall portion 3, and the weight portion 4 are all light in weight, and the dimension in the direction perpendicular to the membrane portion 2 is small. Therefore, the sound insulation structure 1 of this embodiment is light and thin, and as mentioned above, high sound insulation can be obtained in a specific frequency range (for example, below 1000 Hz). Moreover, on a flat loading surface, a loading surface with a curved surface or a concave-convex loading surface, the support wall portion 3 made of a soft material can be easily and stably set even without being fixed by bonding or the like.

[0141] Figure 3A 1 is a perspective view of a sound insulation structure 1 according to a modified example of the first embodiment of the present invention. Figure 3B is Figure 3A A cross-sectional view after cutting along the A-A line and flipping upside down. Figure 4A is a cross-sectional view of a sound insulation structure 1 according to another modified example. Figure 4B It is a perspective view of the weight portion 4 of the sound insulating structure 1. Figure 5A is a cross-sectional view of a sound insulation structure 1 according to yet another modified example. Figure 5B 4 is a perspective view of the weight portion 4 of the sound insulation structure 1. In these modified examples, the spring portion 4a and the mass portion 4b of the weight portion 4 have different shapes and different sizes. Figure 3A , 3B In the modified example shown, the spring portion 4a is a small-diameter cylindrical shape, and the mass portion 4b is a large-diameter cylindrical shape. Figure 4A , 4B In the modified example shown, the spring portion 4a is in the shape of an elongated cylinder, and the mass portion 4b is in the shape of a sphere, and the diameter of the cross-sectional shape of the cylindrical spring portion 4a is smaller than the diameter of the spherical mass portion 4b. Figure 5A , 5B In the modified example shown, the spring portion 4a is truncated cone-shaped, the mass portion 4b is cylindrical, and the diameter of the smallest portion of the truncated cone-shaped spring portion 4a is substantially the same as the diameter of the cylindrical mass portion 4b. Figures 3A to 4B In the modified example shown, the mass portion 4b has a larger volume than the spring portion 4a. Therefore, even if the spring portion 4a and the mass portion 4b are formed of the same material, the mass of the mass portion 4b is larger than the mass of the spring portion 4a, and a spring mass resonator can be formed. However, in this modified example, the spring portion 4a and the mass portion 4b can be formed of different materials, and the mass of the mass portion 4b is larger than the mass of the spring portion. On the other hand, in Figure 5A , 5B In the modified example shown, the spring portion 4a has a larger volume than the mass portion 4b. In this case, the mass portion 4b is formed of a material with a density greater than that of the spring portion 4a, so that the mass of the mass portion 4b is greater than that of the spring portion, and a spring mass resonator can be formed. Figure 5A , 5BWhen the spring portion 4a is formed into a truncated cone shape tapering in the direction away from the diaphragm portion 2 as in the modified example shown, the releasability from the mold when the diaphragm portion 2 and the spring portion 4a are integrally molded is improved.

[0142] In the present embodiment, in the spring portion 4a and the mass portion 4b of the counterweight portion 4, by making either or both of the material and volume different, the mass of the mass portion 4b can be made larger than the mass of the spring portion 4a, forming a spring mass resonator, and obtaining a sufficient sound insulation effect. That is, the material, shape, and size of the spring portion 4a and the mass portion 4b are determined in such a way that a spring mass resonator that can exert a sufficient sound insulation effect can be formed. As long as the mass of the mass portion 4b can be made larger than the mass of the spring portion 4a to the extent that a spring mass resonator that can exert a sufficient sound insulation effect can be formed, the material, shape, and size of the spring portion 4a and the mass portion 4b can be freely selected. However, in order for the spring portion 4a to function as a spring, it is necessary to be formed of a soft material.

[0143] [Second embodiment]

[0144] Fig. 6A 2 is a perspective view of a sound insulation structure 6 according to a second embodiment of the present invention. Figure 6B is Fig. 6A A cross-sectional view after cutting at the A-A line and inverting it upside down. The sound insulation structure 6 has a counterweight portion 7 of a single structure that is not divided into a spring portion and a mass portion. In the present embodiment, a spring mass resonator is formed in which the counterweight portion 7 as a whole functions as a mass portion and the diaphragm portion 2 functions as a spring portion. As an example, the mass of the counterweight portion 7 is about 0.1g to 2.0g. The material of the counterweight portion 7 is not limited, and is formed of, for example, a synthetic resin or a metal. The structure other than this is the same as the first embodiment described above, so the description is omitted. In the sound insulation structure 6 of the present embodiment, the membrane vibration is controlled by the action of the spring mass resonator formed by the counterweight portion 7 and the diaphragm portion 2, and in a specific frequency range (for example, below 1000Hz), the membrane vibration is greatly reduced, and a high sound insulation performance is exerted. In addition, sometimes the air in the space surrounded by the diaphragm portion 2 and the supporting wall portion 3 functions together with the diaphragm portion 2 as a part of the spring (air spring) of the spring mass resonator.

[0145] The membrane portion 2 and the supporting wall portion 3 of the present embodiment preferably have a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and preferably have a loss tangent (tanδ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. Further, the membrane portion 2 and the supporting wall portion 3 of the present embodiment more preferably have a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tanδ) of 0.05 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz.

[0146] In addition, the support wall portion 3 of the present embodiment is composed of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane portion 2 of the present embodiment is also composed of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0147] Fig. 7A is a cross-sectional view of a sound insulating structure 6 according to a modified example of the second embodiment of the present invention. Figure 7B It is a three-dimensional view of the counterweight portion 7 of the sound insulation structure 6. In this modification, the counterweight portion 7 is a truncated cone shape that is tapered in the direction of separation from the diaphragm portion 2. In this structure, when the diaphragm portion 2 and the counterweight portion 7 are integrally formed, the demolding property from the mold is good. In this embodiment, the shape of the counterweight portion 7 can be determined arbitrarily without special limitation.

[0148] In any of the first to second embodiments, the membrane portion 2 and the supporting wall portion 3 can be formed by integral molding or two-color molding of the above-mentioned materials based on injection molding, compression molding, stamping molding, extrusion molding, transfer molding, casting, etc. Furthermore, the weight portions 4 and 7 can sometimes be formed together with the membrane portion 2 and the supporting wall portion 3 by integral molding, two-color molding, or embedded molding of the above-mentioned materials. However, the membrane portion 2, the supporting wall portion 3, and the weight portions 4 and 7 can also be formed separately and then joined to each other by bonding or heat sealing, thereby assembling the sound insulation structures 1 and 6.

[0149] In the structures of the sound insulation structures 1 and 6 described above, Fig. 8A , 8BAs shown, the support wall portion 3 includes a plurality of first wall portions 3a extending along a first direction D1 parallel to the membrane portion 2 and a plurality of second wall portions 3b extending along a second direction D2 orthogonal to the first direction D1, and the planar shape of each partition 5 is a square. In other words, the support wall portion 3 is a square tube having a square cross-sectional shape that divides each partition 5, and a plurality of square tube-shaped support wall portions 3 are arranged, and the support wall portions 3 of adjacent partitions 5 are integrated. However, the structure is not limited to this. For example, it can also be as follows Fig. 9A , 9B As shown in FIG. 1 , the planar shape of each partition 5 is a triangle, and the support wall portion 3 is a square tube having a triangular cross-sectional shape that divides each partition 5. Fig. 10A , 10B As shown, the planar shape of each partition 5 is a pentagon, and the support wall portion 3 is a square tube having a cross-sectional shape of a pentagon that divides each partition 5. Fig.11A , 11B As shown, the planar shape of each partition 5 is a hexagon, and the support wall portion 3 is a square tube having a hexagonal cross-sectional shape that divides each partition 5, forming a so-called honeycomb structure. Fig. 12A , 12B As shown, the planar shape of each partition 5 is circular, and the support wall portion 3 is cylindrical with a circular cross-sectional shape that divides each partition 5. Fig. 10A , 10B In the case of the structures shown in 12A and 12B, gaps are generated between the partitions 5, so it is preferable to determine the shape and size of the support wall 3 so as to reduce the gaps. Fig. 8A , 8B , 9A, 9B, 11A, 11B, there is no gap between the partitions 5. Moreover, each partition 5 may be in various shapes not shown, such as a rectangle, a parallelogram, a trapezoid, a polygon with a heptagon or more, an ellipse, an oblong, etc., or an irregular shape. The support wall portion 3 is formed in a shape and size consistent with the planar shape of each partition 5.

[0150] The sound insulation structures 1 and 6 of the present invention are very thin and light, and can be easily placed on a curved or uneven surface. Therefore, they can also be placed on the panels of passenger vehicles, especially automobiles, for use. The panels of automobiles and the like are usually non-breathable plates, and as an example, metal plates (iron plates, steel plates, aluminum plates), resin plates, etc. can be cited. In the case where the panel on which the sound insulation structure 1 is placed is a metal plate, its thickness is preferably in the range of 0.5 mm to 2.0 mm, and in the case of a resin plate, its thickness is preferably in the range of 0.5 mm to 20 mm. In the case of placing the sound insulation structures 1 and 6 on the panel of the automobile, it is preferred that the end face of the supporting wall portion 3 of the sound insulation structure 1 and 6 on the side opposite to the side mounted on the membrane portion 2 is placed on the panel. In addition, at this time, the supporting wall portion 3 and the panel may be bonded or not bonded, but it is preferred that the supporting wall portion 3 is placed on the panel for use without being bonded to the panel.

[0151] In addition, the sound insulation structures 1, 6 of the present invention can be used alone or in combination with other components (not shown). When the sound insulation structures 1, 6 of the present invention are used in combination with other components, they can be stacked or combined with other components. When stacked or combined with other components, the sound insulation structures 1, 6 can be placed in contact with the sound insulation structures 1, 6 at the location where the sound insulation structures 1, 6 are placed (for example, the panel of a car), or they can be placed in contact with other components at that location. Other components used in combination with the sound insulation structures 1, 6 can be made of various materials.

[0152] As the parts where the sound insulation structures 1 and 6 of the present invention are arranged in the automobile, in the engine compartment, there can be listed the engine hood, the engine body hood, the engine hood vibration isolation pad, the front vibration isolation pad of the dash panel, the wall of the air box, the air intake cleaner, the dust side duct, the lower cover, etc.; in the cab, there can be listed the dash panel vibration isolation pad, the dash panel panel, the floor carpet (floor silencer), the spacer, the door decoration of the door, the interior of the door decoration, the installation panel, the installation center box, the installation upper box, the box body of the air conditioner, the roof decoration, the interior of the roof decoration, the sun visor, the rear seat air conditioning duct, the cooling duct of the battery cooling system in the battery-mounted vehicle, the cooling fan, the center console decoration, the interior of the console, the storage board decoration, the storage board panel, the seat headrest, the front seat backrest, the rear seat backrest, etc.; in the trunk, there can be listed the trunk side decoration, the interior of the decoration, the car ventilator cover, etc. In addition, the sound insulation structures 1, 6 of the present invention can also be set in the frame or between panels of the car. Furthermore, they can also be set in the lower cover under the floor outside the car, the fender protector, the rear door, the wheel cover, the aerodynamic cover of the suspension, etc.

[0153] Specific examples and comparative examples of the sound insulating structure of the present invention will be described below.

[0154] [Example 1]

[0155] The sound insulation structure 1 of the embodiment 1 of the present invention is Figures 1A to 2B The membrane 2 is made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa to 100 MPa at 23°C and a frequency of 1 Hz to 1000 Hz and a loss tangent (tan δ) of 0.01 to 0.50 at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the membrane portion 2 of the present embodiment is composed of EPDM (ethylene-propylene-diene rubber), and the dynamic storage modulus (E') of the EPDM (ethylene-propylene-diene rubber) at 23°C and a frequency of 1 Hz is 20.4 MPa and the loss tangent (tan δ) is 0.12, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 23.0 MPa and the loss tangent (tan δ) is 0.13, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 25.4 MPa and the loss tangent (tan δ) is 0.16, the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 28.8 MPa and the loss tangent (tan δ) is 0.14, the durometer A hardness based on JIS K6253 is 70, and the film thickness is 0.5 mm. The planar shape of the membrane portion 2 is 1000 cm 2 In the case of a square area, the bending rigidity K is 67.2N / mm 2 , in plane shape 400cm 2 In the case of a square area, the bending rigidity K is 42.5N / mm 2 Assume that a film having a thickness of 3 mm and a planar shape of 1000 cm is formed from the same material as the film portion 2. 2 In the case of a square membrane portion, its bending rigidity K is about 1.5×10 4 N / mm 2 .

[0156] The supporting wall 3 of the present embodiment is made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa to 100 MPa at 23°C and a frequency of 1 Hz to 1000 Hz and a loss tangent (tan δ) of 0.01 to 0.50 at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the support wall portion 3 of the present embodiment is made of EPDM, and the dynamic storage modulus (E') of the EPDM at 23°C and a frequency of 1 Hz is 13.2 MPa and the loss tangent (tan δ) is 0.12, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 15.0 MPa and the loss tangent (tan δ) is 0.14, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 17.4 MPa and the loss tangent (tan δ) is 0.17, the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 20.2 MPa and the loss tangent (tan δ) is 0.16, the durometer A hardness based on JIS K6253 is 65, the plate thickness is 1.6 mm, and the height in the direction orthogonal to the membrane portion 2 is 10 mm. However, the plate thickness of the support wall portion 3 located only on the outermost side is half, that is, 0.8 mm. The partitions 5 divided by the plurality of supporting walls 3 (the first wall 3a and the second wall 3b) are 25 mm × 25 mm squares, and there are 49 partitions 5 in the 200 mm × 200 mm square area (evaluation surface) of the membrane 2. However, only a part of the area is schematically shown in the drawing. The counterweight 4 is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane 2) of 6 mm.

[0157] The portion of the counterweight portion 4 installed on one side of the diaphragm portion 2, namely the spring portion 4a, has a height of 3 mm and is composed of an elastomer having a dynamic storage modulus (E') of greater than 0.01 MPa and less than 100 MPa at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tanδ) of greater than 0.01 and less than 0.50 at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the spring portion 4a of the present embodiment is made of silicone rubber, and the dynamic storage modulus (E') of the silicone rubber at 23°C and a frequency of 1 Hz is 0.60 MPa and the loss tangent (tan δ) is 0.17, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 0.74 MPa and the loss tangent (tan δ) is 0.24, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 0.97 MPa and the loss tangent (tan δ) is 0.17, the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 1.31 MPa and the loss tangent (tan δ) is 0.16, and the durometer A hardness based on JIS K6253 is 10. The portion of the weight portion 4 on the side opposite to the side mounted on the diaphragm portion 2, that is, the mass portion 4b, is also 3 mm in height and is made of rigid stainless steel (SUS304). The mass of the weight portion 4 is about 0.8 g, and has a resonance with a peak value at a frequency of 600 Hz to 650 Hz relative to the direction perpendicular to the installation surface of the weight portion 4. The overall height of the sound insulation structure 1 is 10.5 mm, and the overall surface density of one partition 5 including the membrane portion 2, the support wall portion 3, and the weight portion 4 is 2.97 kg / m 2 .

[0158] like Fig.13 As shown, the end face of the supporting wall portion 3 of the sound insulating structure 1 on the side opposite to the side mounted on the membrane portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm, and the surface of the iron plate 8 on the side opposite to the side on which the sound insulating structure 1 is placed is used as the incident sound side to measure the sound insulation. Specifically, based on the intensity method shown in JISA1441-1, a test equipment room in which the sound source room is a reverberation room and the sound receiving room is a semi-anechoic room is used to determine the sound transmission loss (transmission loss) [dB] relative to the 1 / 3 octave band center frequency [Hz] through 1 / 3 octave band analysis. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is determined and shown. Figures 14A to 14F , 14K. The greater the sound transmission loss, the higher the sound insulation. Figures 14A to 14K In the 1 / 3 octave band center frequencies [Hz] shown, 1kHz is 1000Hz and the prefix "k" refers to 1000.

[0159] [Comparative Example 1]

[0160] As Comparative Example 1, Fig.15As shown, the sound insulation is measured in a state where nothing is placed on an iron plate 8 having a thickness of 0.8 mm, and Fig.14A The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown. This indicates the state where no sound insulation structure is set. The surface density of this structure is 6.02kg / m 2 .

[0161] [Comparative Example 2]

[0162] As Comparative Example 2, a theoretical value of sound insulation performance calculated based on the mass law was obtained when a component having the same mass as the sound insulation structure 1 of Example 1 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was calculated based on the mass law. Fig.14A The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in the figure. The surface density of the structure is 8.99 kg / m 2 .

[0163] [Comparative Example 3]

[0164] As Comparative Example 3, Fig.16A , 16B As shown in FIG. 1 , a sound insulation structure consisting of only the membrane portion 2 and the support wall portion 3 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was measured. Figures 14A to 14B The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in FIG. The membrane 2 and the supporting wall 3 of this embodiment are the same as those of the membrane 2 and the supporting wall 3 of the embodiment 1, but do not have the counterweight 4. The surface density of this structure is 2.43 kg / m 2 .

[0165] [Example 2]

[0166] The sound insulation structure 6 of the second embodiment of the present invention is Fig. 6A , 6B The structure is the same as the second embodiment shown. The membrane portion 2 and the supporting wall portion 3 of this embodiment are the same as the membrane portion 2 and the supporting wall portion 3 of the embodiment 1. In addition, the counterweight portion 7 is composed of EPDM with a durometer A hardness of 65 based on JIS K6253-3, and is a cylindrical shape with a diameter of 13 mm and a height (dimension in the direction perpendicular to the membrane portion 2) of 5 mm. The mass of the counterweight portion 7 is about 0.85 g, and the surface density of the structure is 3.04 kg / m 2 .like Fig.17 As shown, the end surface of the supporting wall portion 3 of the sound insulation structure 6 opposite to the side mounted on the membrane portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance is obtained and is shown in FIG. Fig. 14B .

[0167] [Example 3]

[0168] Fig.18A , 18BThe sound insulation structure 6 of the embodiment 3 of the present invention shown has the same structure as that of the embodiment 2, but has a counterweight portion 7 that is smaller than the counterweight portion 7 of the embodiment 2. The diaphragm portion 2 and the supporting wall portion 3 of this embodiment are the same as the diaphragm portion 2 and the supporting wall portion 3 of the embodiment 1. The counterweight portion 7 is made of EPDM with a durometer A hardness of 65 based on JIS K6253-3, and is cylindrical with a diameter of 6 mm and a height (dimension in a direction perpendicular to the diaphragm portion 2) of 5 mm. The mass of the counterweight portion 7 is about 0.15 g. The surface density of the structure is 2.54 kg / m 2 .like Fig.18B As shown, the end surface of the supporting wall portion 3 of the sound insulation structure 6 opposite to the side mounted on the membrane portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance is obtained, and is shown in FIG. Fig. 14B .

[0169] [Example 4]

[0170] The sound insulation structure 1 (not shown) of Example 4 of the present invention has the same structure as that of Example 1, but has a support wall portion 3 that is softer than the support wall portion 3 of Example 1. The diaphragm portion 2 and the weight portion 4 of this embodiment are the same as the diaphragm portion 2 and the weight portion 4 of Example 1. The support wall portion 3 of this embodiment is composed of an elastomer having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tanδ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the support wall portion 3 of the present embodiment is made of EPDM, and the dynamic storage modulus (E') of the EPDM at 23°C and a frequency of 1 Hz is 1.48 MPa and the loss tangent (tan δ) is 0.07, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 1.72 MPa and the loss tangent (tan δ) is 0.12, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 2.00 MPa and the loss tangent (tan δ) is 0.11, the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 2.33 MPa and the loss tangent (tan δ) is 0.12, the durometer A hardness based on JIS K6253-3 is 30, the plate thickness is 1.6 mm, and the height in the direction orthogonal to the membrane portion 2 is 10 mm. However, the plate thickness of the support wall portion 3 located only on the outermost side is half, that is, 0.8 mm. The surface density of the structure is 2.52 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig. 14C .

[0171] [Comparative Example 4]

[0172] The sound insulation structure (not shown) of Comparative Example 4 is substantially the same structure as that of Example 1, but has a support wall 3 that is harder and less flexible than the support wall 3 of Example 1. The diaphragm 2 and weight 4 of this comparative example are the same as those of Example 1. The supporting wall 3 of this comparative example is made of polylactic acid (PLA resin), and its shape and size are the same as those of the supporting wall 3 of Example 1. The dynamic storage modulus (E') of the polylactic acid (PLA resin) at 23°C and a frequency of 1Hz is 2.03GPa and the loss tangent (tanδ) is 0.0045, the dynamic storage modulus (E') at 23°C and a frequency of 10Hz is 2.04GPa and the loss tangent (tanδ) is 0.000060, the dynamic storage modulus (E') at 23°C and a frequency of 100Hz is 2.05GPa and the loss tangent (tanδ) is 0.045, and the dynamic storage modulus (E') at 23°C and a frequency of 1000Hz is 2.07GPa and the loss tangent (tanδ) is 0.0079. The surface density of the structure is 2.63kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig. 14C .

[0173] [Example 5]

[0174] The sound insulation structure 1 (not shown) of Example 5 is of the same structure as that of Example 1, but has a diaphragm 2 that is softer than that of Example 1. The supporting wall 3 and the counterweight 4 of this example are the same as those of Example 1. The diaphragm 2 of this example is made of the same material as that of the supporting wall 3 of Example 4 and is made of EPDM having a durometer A hardness of 30 based on JIS K6253-3, and has the same shape and size as those of the diaphragm 2 of Example 1. The surface density of the structure is 2.83 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14D .

[0175] [Example 6]

[0176] Fig.19A , 19BThe sound insulation structure 1 of the sixth embodiment shown has the same structure as that of the first embodiment, but has a partition 5 that is larger than the partition 5 of the first embodiment. The membrane 2 and the weight 4 of the present embodiment are the same as those of the first embodiment. Moreover, the supporting wall 3 of the present embodiment is the same as the supporting wall 3 of the first embodiment, but is arranged at a larger interval than that of the first embodiment. As a result, each partition of the present embodiment is a square shape of 50 mm×50 mm, and its area is 2500 mm. 2 The surface density of the structure is 1.60kg / m 2 There are nine partitions 5 in a 200 mm x 200 mm square region (evaluation surface) of the membrane portion 2. However, only a portion of this region is schematically shown in the drawing. Fig.19B As shown in FIG. 1 , the end surface of the supporting wall portion 3 of the sound insulation structure opposite to the side mounted on the membrane portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance is obtained, and is shown in FIG. Fig.14E .

[0177] [Example 7]

[0178] The sound insulation structure 1 (not shown) of Example 7 is the same structure as that of Example 1, but the weight portion 4 is a cylindrical shape having a diameter of 13 mm and a height (dimension in a direction perpendicular to the diaphragm portion 2) of 9 mm. The portion of the weight portion 4 mounted on one side of the diaphragm portion 2, i.e., the spring portion 4a, has a height of 4 mm and is composed of an elastic body having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tanδ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the spring portion 4a of the present embodiment is composed of polyurethane foam, and the dynamic storage modulus (E') of the polyurethane foam at 23°C and 1 Hz is 0.06 MPa and the loss tangent (tan δ) is 0.15, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 0.07 MPa and the loss tangent (tan δ) is 0.15, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 0.08 MPa and the loss tangent (tan δ) is 0.15, and the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 0.10 MPa and the loss tangent (tan δ) is 0.15. The portion of the weight portion 4 on the side opposite to the side mounted on the membrane portion 2, that is, the mass portion 4b has a height of 5 mm and is composed of EPDM having a durometer A hardness of 65 based on JIS K6253-3. The mass of the weight portion 4 is approximately 1.0 g.

[0179] The membrane 2 and the supporting wall 3 of this embodiment are the same as those of the embodiment 1. The surface density of this structure is 3.08 kg / m2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14F .

[0180] [Example 8]

[0181] The sound insulation structure 1 (not shown) of Example 8 is Figure 3A , 3B The structure is the same as the modified example of the first embodiment shown. The diaphragm portion 2 and the supporting wall portion 3 of this embodiment are the same as the diaphragm portion 2 and the supporting wall portion 3 of Example 1, but the counterweight portion 4 of this embodiment is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The portion of the counterweight portion 4 installed on one side of the diaphragm portion 2, namely the spring portion 4a, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the diaphragm portion 2) of 3 mm, and is composed of the same material as the spring portion 4a of the counterweight portion 4 of Example 1 (silicone rubber with a durometer A hardness of 10 based on JIS K6253-3). The portion of the counterweight portion 4 on the side opposite to the side installed on the diaphragm portion 2, namely the mass portion 4b, is cylindrical with a diameter of 13 mm and a height of 5 mm, and is composed of EPDM with a durometer A hardness of 65 based on JIS K6253-3. The mass of the counterweight portion 4 is about 1.0 g. The surface density of the structure is 3.13 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Figures 14F to 14G .

[0182] [Example 9]

[0183] The sound insulation structure 1 (not shown) of Example 9 is Figure 3A , 3B The membrane 2 and the weight 4 of this embodiment are the same as those of the embodiment 8, but the support wall 3 of this embodiment is made of EPDM having a hardness of 30 according to JIS K6253, a thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the membrane 2. The surface density of this structure is 2.81 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Figures 14G to 14I .

[0184] [Example 10]

[0185] Fig. 20 The sound insulation structure 1 of the embodiment 10 shown is Figure 3A , 3B The membrane 2 and the weight 4 of this embodiment are the same as those of the embodiment 9, but the support wall 3 of this embodiment is made of EPDM having a hardness of 30 according to JIS K6253, a thickness of 1.6 mm, and a height of 14 mm in a direction perpendicular to the membrane 2. The surface density of this structure is 3.16 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14H .

[0186] [Example 11]

[0187] Fig.21A , 21B The sound insulation structure 1 of the embodiment 11 shown is Figure 3A , 3B The structure is the same as that of the modification of the first embodiment shown. Fig.21A is a three-dimensional diagram of the sound insulation structure 1. Fig. 21B It is a cross-sectional view cut along the BB line. The diaphragm 2 and the weight 4 of this embodiment are the same as those of the diaphragm 2 and the weight 4 of the embodiment 9, but in this embodiment, the height of a part of the supporting wall 3d extending in the direction perpendicular to the diaphragm 2 is higher than the height of the other supporting wall 3c. That is, the sound insulation structure 1 of this embodiment has a supporting wall (a part of the supporting wall) 3d which is the same as the supporting wall 3 of the embodiment 10 and has a high height, and a supporting wall (another supporting wall) 3c which is the same as the supporting wall 3 of the embodiment 9 and has a low height. Specifically, the supporting wall 3c is composed of EPDM having a hardness of 30 in the durometer A based on JIS K6253, a thickness of 1.6 mm, and a height of 10 mm in the direction perpendicular to the diaphragm 2, and the supporting wall 3d is composed of EPDM having a hardness of 30 in the durometer A based on JIS K6253, a thickness of 1.6 mm, and a height of 15 mm in the direction perpendicular to the diaphragm 2. The support wall portion 3d has a height 1.5 times that of the support wall portion 3c. Fig.21A , 21B As shown in FIG. 1 , rows with high support walls 3d and rows with low support walls 3c are arranged alternately. Thus, 16 of the 49 square sections 5 arranged in a 7×7 grid are sections surrounded by high support walls 3d. The surface density of this structure is 3.02 kg / m 2 The end surface of the supporting wall portion 3d of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14I .

[0188] [Example 12]

[0189] The sound insulation structure 1 (not shown) of Example 12 is Figure 3A , 3B The weight portion 4 of this embodiment is the same as the weight portion 4 of Example 8. The membrane portion 2 and the support wall portion 3 of this embodiment are formed by integrally molding a styrene-based thermoplastic elastomer (TPS), which has a dynamic storage modulus (E') of 7.81 MPa and a loss tangent (tan δ) of 0.06 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 8.62 MPa and a loss tangent (tan δ) of 0.08 at 23°C and a frequency of 10 Hz, and a dynamic storage modulus (E') of 7.81 MPa and a loss tangent (tan δ) of 0.06 at 23°C and a frequency of 10 Hz. The dynamic storage modulus (E') at 0 Hz is 9.19 MPa and the loss tangent (tanδ) is 0.11, the dynamic storage modulus (E') at 23 ° C and a frequency of 1000 Hz is 10.3 MPa and the loss tangent (tanδ) is 0.08, the durometer A hardness based on JIS K6253 is 50, the thickness of the membrane 2 is 1.0 mm, the plate thickness of the supporting wall 3 is 1.2 mm, and the height in the direction orthogonal to the membrane 2 is 10 mm. The surface density of the structure is 2.56 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14J .

[0190] [Example 13]

[0191] The sound insulation structure 1 (not shown) of Example 13 is Figure 3A , 3BThe diaphragm 2 and the supporting wall 3 of this embodiment are the same as those of the diaphragm 2 and the supporting wall 3 of the embodiment 12. The weight 4 of this embodiment is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The portion of the counterweight portion 4 installed on one side of the diaphragm portion 2, namely the spring portion 4a, is composed of TPS, which is a cylindrical shape with a diameter of 6 mm and a height (dimension in the direction perpendicular to the diaphragm portion 2) of 3 mm, and has a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tanδ) of 0.03 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tanδ) of 0.03 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tanδ) of 0.04 at 23°C and a frequency of 100 Hz, a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tanδ) of 0.25 at 23°C and a frequency of 1000 Hz, and a dynamic storage modulus (E') of 0.23 MPa and a loss tangent (tanδ) of 0.04, and a durometer A hardness based on JIS K6253 of 0. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side mounted on the diaphragm portion 2, is cylindrical with a diameter of 11 mm and a height of 6 mm and is made of EPDM with a durometer A hardness of 70 based on JIS K6253-3. The surface density of this structure is 2.50 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14J .

[0192] [Example 14]

[0193] The sound insulation structure 1 (not shown) of Example 13 is Figure 3A , 3BThe diaphragm portion 2 and the supporting wall portion 3 of the present embodiment are the same as those of the diaphragm portion 2 and the supporting wall portion 3 of the embodiment 12. The counterweight portion 4 of the present embodiment is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The portion of the counterweight portion 4 installed on one side of the diaphragm portion 2, i.e., the spring portion 4a, is a cylindrical shape having a diameter of 6 mm and a height (dimension in a direction perpendicular to the diaphragm portion 2) of 3 mm. The portion of the counterweight portion 4 on the side opposite to the side installed on the diaphragm portion 2, i.e., the mass portion 4b, is a cylindrical shape having a diameter of 9 mm and a height of 6 mm. The spring portion 4a and the mass portion 4b of the counterweight portion 4 of this embodiment are composed of TPS, and the dynamic storage modulus (E') of the TPS at 23°C and a frequency of 1 Hz is 0.21 MPa and the loss tangent (tanδ) is 0.04, the dynamic storage modulus (E') at 23°C and a frequency of 10 Hz is 0.23 MPa and the loss tangent (tanδ) is 0.03, the dynamic storage modulus (E') at 23°C and a frequency of 100 Hz is 0.29 MPa and the loss tangent (tanδ) is 0.05, the dynamic storage modulus (E') at 23°C and a frequency of 1000 Hz is 0.25 MPa and the loss tangent (tanδ) is 0.17, and the durometer A hardness based on JIS K6253 is 5. The surface density of the structure is 2.50 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Fig.14J .

[0194] [Comparative Example 5]

[0195] As Comparative Example 5, similarly to Comparative Example 3, Fig.16A , 16B As shown in FIG. 1 , a sound insulation structure consisting of only the membrane portion 2 and the supporting wall portion 3 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was measured. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in FIG. Fig.14J The membrane 2 and the supporting wall 3 of this embodiment are different from those of the embodiment 1 and the comparative example 3, and are the same as those of the embodiment 12. Moreover, the sound insulation structure of this comparative example does not have the weight portion 4. The surface density of the structure is 1.88 kg / m 2 .

[0196] [Comparative Example 6]

[0197] The sound insulation structure 1 (not shown) of Comparative Example 6 is of the same structure as that of Example 1, but has a membrane portion 2 made of a resin material having a thinner membrane thickness than that of the membrane portion 2 of Example 1. The supporting wall portion 3 and the counterweight portion 4 of this embodiment are the same as the supporting wall portion 3 and the counterweight portion 4 of Example 1. The membrane portion 2 of this comparative example is made of low-density polyethylene (LDPE) having a membrane thickness of 0.05 mm. The surface density of the structure is 2.25 kg / m 2 The end surface of the supporting wall portion 3 of the sound insulation structure 1 on the side opposite to the side mounted on the membrane portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation performance was obtained and is shown in FIG. Figure 14K .

[0198] [result]

[0199] The results of comparison between Examples 1 to 14 of the present invention and Comparative Examples 1 to 6 described above will be described. Fig.14A , it can be seen that the sound insulation effect is improved by the sound insulation structure 1 of the present invention. In particular, it can be seen that according to the sound insulation structure 1 of Example 1, in the frequency band higher than 630Hz, a significantly larger sound insulation effect can be obtained than the theoretical value based on the mass law (Comparative Example 2), and the effect of the present invention is large. Moreover, it can be seen that, especially in the frequency band lower than 1.25kHz, when compared with Comparative Example 3, the sound insulation property of Example 1 having the weight portion 4 is large.

[0200] Reference Fig. 14B It can be seen that in the sound insulation structure 1 of the first embodiment of the present invention (Example 1) and the sound insulation structure 6 of the second embodiment (Examples 2 and 3), good sound insulation effects can be obtained in the same manner. In addition, as shown in Example 1, when the weight portion 4 itself constitutes a spring mass resonator, by the resonance of the spring mass resonator, particularly good sound insulation can be obtained near the frequency (for example, 630 Hz to 1000 Hz) at which the vibration of the diaphragm portion 2 is reduced. On the other hand, when the spring mass resonator is constituted by the weight portion 7 and the diaphragm portion 2 as in Examples 2 and 3, the frequency band in which the sound insulation is particularly good can be adjusted by the weight of the weight portion 7. For example, when the weight portion 7 has the same mass as the weight portion 4 of Example 1, the frequency band in which the sound insulation is particularly good is near 1000 Hz. When the weight portion 7 is lightened, the frequency band in which the sound insulation is particularly good can be moved to the high frequency side.

[0201] Reference Fig. 14CIt can be seen that when the supporting wall portion 3 of the sound insulation structure is not made of a soft material, the sound insulation is low, but when the supporting wall portion 3 is made of a soft material, a good sound insulation effect can be obtained. This is considered to be because when the supporting wall portion 3 is not made of a soft material but is a harder component, the vibration is easily transmitted to the membrane portion 2 via the supporting wall portion 3, and on the contrary, when the supporting wall portion 3 is made of a soft material, the vibration is difficult to be transmitted to the membrane portion 2 via the supporting wall portion 3. In addition, by adjusting the hardness of the supporting wall portion 3, the frequency band with particularly good sound insulation can be adjusted. For example, when the supporting wall portion 3 is made softer, the frequency band with particularly good sound insulation can be moved to the low frequency side.

[0202] Reference Fig.14D It is known that when the diaphragm 2 of the sound insulating structure is too soft, the sound insulating property is slightly reduced. This is considered to be because when the diaphragm 2 is too soft, the vibration of the spring mass resonator cannot be transmitted to the spring mass resonator to a degree that allows the spring mass resonator to fully function.

[0203] Reference Fig.14E It is known that when each partition 5 of the membrane portion 2 divided by the supporting wall portion 3 of the sound insulation structure is too large, the sound insulation performance is slightly reduced. It is believed that when each partition 5 is too large, the spring mass resonator cannot fully function and the vibration reduction effect is weakened. Therefore, it is preferred that each partition 5 is smaller to a certain extent (for example, 1000mm 2 the following).

[0204] Reference Fig.14F It is known that even if the material and shape of the weight 4 of the sound insulating structure 1 are different, the sound insulating function of the present invention can be exhibited as long as the material and shape are within the preferred range. Therefore, it is known that the material and shape of the weight 4 can be freely set within the preferred range.

[0205] Reference Figure 14G It can be seen that even if the Durometer A hardness of the support wall portion 3 according to JIS K6253-3 is different to some extent, the same sound insulation effect can be obtained. Fig.14H It can be seen that a good sound insulation effect can be obtained by a structure in which the height of the supporting wall portion 3 is relatively high and extends in a direction perpendicular to the membrane portion 2. This is because when the height of the supporting wall portion 3 is relatively high, the thickness of the air layer between the mounting surface (in each embodiment, the iron plate 8) on which the sound insulation structure 1, 6 is mounted and the membrane portion 2 is relatively thick, so the frequency band of the resonance transmission of the air changes, and the effect of the sound insulation obstruction in the target frequency band is reduced, especially the sound insulation amount in the low frequency range (for example, around 500 Hz) becomes larger.

[0206] Reference Fig.14IIt can be seen that even if the height of only a part of the supporting wall portions 3d extending in the direction orthogonal to the membrane portion 2 is increased among the multiple supporting wall portions, and the height of the other supporting wall portions 3c is made lower, a good sound insulation effect can be obtained. Even if the height of only a part of the supporting wall portions 3d is higher, the thickness of the air layer between the mounting surface (in each embodiment, the iron plate 8) on which the sound insulation structure 1, 6 is mounted and the membrane portion 2 is increased, just like the structure in which the height of all the supporting wall portions 3d is higher, so as described above, the sound insulation volume in the low frequency domain (for example, near 500Hz) is increased. Moreover, by increasing the height of only a part of the supporting wall portions 3d, it is possible to increase the thickness of the air layer while suppressing the increase in the overall weight of the sound insulation structure 1, 6, and it is easy to stably place the sound insulation structure 1, 6 on a mounting surface of various shapes, such as a curved surface. That is, it is possible to improve the sound insulation performance of the lightweight sound insulation structure 1, 6 with good low-frequency domain. In addition, if there are too few high support walls 3d, it will be difficult to indicate the stability of the sound insulation structure 1, 6, and if there are too many, the weight of the entire sound insulation structure 1, 6 will increase. Therefore, it is preferred that the area 5 surrounded by the high support walls 3d is more than 5% of the total area 5 of the sound insulation structure 1, 6. In addition, it is preferred that, when observing the cross-section of each support wall 3c, 3d parallel to the membrane 2, the total cross-sectional area of ​​the high support wall 3d is more than 10% of the total cross-sectional area of ​​all the support walls 3c, 3d of the sound insulation structure 1, 6. In Example 11, in the 20mm×20mm (area 400cm2) of the membrane 2 having a planar shape of a square of 25mm×25mm 2 ) area, such as Fig.21A As shown, 7×7=49 sections 5 are provided, and 16 of these sections 5 are sections 5 surrounded by the high support wall portion 3 d , so the ratio is preferably 32.6%.

[0207] In addition, in the case where the height of all the supporting wall portions 3 is high as in Example 10 and in the case where the height of only a part of the supporting wall portions 3d is high as in Example 11, it is preferred to make the overall height of the sound insulation structures 1, 6 less than 20 mm as described above to suppress the increase in the overall weight of the sound insulation structures 1, 6 or the limitation of their setting.

[0208] Reference Fig.14JIt can be seen that even if the membrane portion 2 and the supporting wall portion 3 are formed by integral molding of thermoplastic material, good sound insulation can be obtained by providing the counterweight portion 4. It can be seen that, as shown in Example 13, in the spring mass resonator composed of the spring portion 4a and the mass portion (mass block portion) 4b of the counterweight portion 4, when the spring portion 4a is softer, the resonance frequency moves to the low frequency side, and a large sound insulation effect is obtained on the low frequency side. By changing the structure of the counterweight portion 4 in this way, the sound insulation band can be adjusted. In addition, it can be seen that even if the counterweight portion 4 is made of a single material as in Example 14, good sound insulation can be obtained. However, by using a single material to make the counterweight portion, productivity can be improved.

[0209] Reference Figure 14K It is known that when the diaphragm 2 is composed of a thin resin material (film), the sound insulation property is reduced, so it is preferred that the diaphragm 2 has a certain degree of thickness. It is considered that the resin material such as LDPE of Comparative Example 6 is harder than the elastomer material such as EPDM of Example 1, so the film thickness is reduced, but when the film thickness is not above a certain level, the diaphragm 2 is too soft and the vibration of the spring mass resonator composed of the spring part 4a and the mass part (mass block part) 4b of the weight part 4 cannot be transmitted to the weight part 4. Therefore, it is preferred that the diaphragm 2 has a certain degree of thickness.

[0210] [Soundproof structure]

[0211] A soundproofing structure 11 which includes the above-described soundproofing structures 1 and 6 of the present invention and has further improved soundproofing properties and is easy to install will be described. First, Fig. 22 FIG. 1 is a side view of a car as an example of a passenger vehicle provided with the soundproof structure 11. The soundproof structure 11 of the present invention is arranged so as to overlap with a panel (front panel) 14 provided at the boundary between an engine compartment 12 and a passenger compartment 13 of the car. FIG. 1 is a side view of the soundproof structure 11. Fig.23 , the stereogram viewed from the front side is shown in Fig.24 , Fig.24 The C-C line cross-sectional view is shown in Fig.25 . The soundproof structure 11 is composed of a soundproof plate-like portion 10 and a soundproofing structure portion 9 arranged in a plane. The soundproofing structure portion 9 has the same structure as any one of the above-mentioned soundproofing structures 1 and 6 of the present invention. That is, the soundproofing structure portion 9 is composed of any one of the above-mentioned soundproofing structures 1 and 6 of the present invention. In this example, the large-area soundproofing plate-like portion 10 and the two soundproofing structures 9 are formed into one body, or are joined to each other to form a soundproofing structure 11 that can be handled as a single component.

[0212] The soundproof plate-like portion 10 has a single-layer structure consisting of any one of a layer including a sound-absorbing material such as felt, polyurethane foam, and glass wool and a layer including a sound-insulating material such as a resin film and a rubber sheet, or a laminated structure thereof. The soundproof plate-like portion 10 is a plate-like component along the shape of the panel 14, and the thickness may vary depending on the location. As an example, the soundproof plate-like portion 10 has a thinner portion with a thickness of less than 5 mm and a thicker portion with a thickness of about 40 mm. The soundproof plate-like portion 10 may also be a structure substantially the same as or similar to the dash muffler described in Patent Documents 1 and 2.

[0213] An example of the sound insulation structure 9 is Figures 1A to 2B The sound insulation structure 9 has the same structure as the sound insulation structure 1 shown in the figure, that is, the sound insulation structure 9 is composed of the sound insulation structure 1 of the present invention described above. The sound insulation structure 9 has: a thin plate-shaped membrane portion 2 with elasticity; a supporting wall portion 3 that is substantially vertically erected from the membrane portion 2 and has elasticity; and a weight portion 4 that is substantially vertically erected from the membrane portion 2 and has elasticity. The weight portion 4 located in each partition 5 is respectively constituted as a spring mass resonator having an elastic spring portion 4a and a mass portion (mass block portion) 4b with a mass greater than the mass of the spring portion 4a. The sound insulation structure 9 is Figures 1A to 2B The structure is the same as the sound insulation structure 1 shown in the figure, so as described above, the vibration of the membrane portion 2 is controlled by the action of the spring mass resonator composed of the spring portion 4a and the mass portion 4b of the weight portion 4. In particular, in a specific frequency range (for example, a frequency below 1000 Hz), the membrane vibration is greatly reduced, and a high sound insulation performance can be exerted.

[0214] In the soundproof structure 11, the soundproofing structure 9 having the above-mentioned structure is arranged at a location where sound propagation is particularly large in a passenger vehicle or the like. Fig. 22In the example shown, the soundproof structure 11 is arranged so as to overlap with the panel 14 located at the boundary between the engine compartment 12 and the vehicle compartment 13 of the automobile. In addition, the soundproofing structure 9 is respectively arranged at two locations opposite to the front tires, where the road noise is sometimes transmitted greatly. Assuming that the soundproofing structure 11 arranged in a manner overlapping with the panel 14 is composed of the soundproofing structure 9 of the above-mentioned structure as a whole, the soundproofing effect is high, but the weight of the soundproofing structure 11 is large, and there is a problem of adversely affecting the performance of the vehicle. In contrast, in the soundproofing structure 11 of the present embodiment, the soundproofing structure 9 with a large soundproofing effect is particularly arranged at a location where the sound is transmitted greatly (for example, a location opposite to the tire), and the soundproofing plate-shaped portion 10 with a simple structure is arranged at a location where the sound is not transmitted so greatly (a location other than the location opposite to the tire). As a result, it is possible to suppress the entry of sound efficiently while suppressing the increase in weight to a small extent. Furthermore, not only the soundproof plate-shaped portion 10 formed in accordance with the shape of the panel 14, but also the soundproof structural portion 9 can be easily and stably installed on mounting surfaces of various shapes without being fixed by bonding, etc. Therefore, the soundproof structure 11 of this embodiment can be stacked on a panel 14 of a complex shape and stably maintained.

[0215] In this example, on one main surface of the soundproof structure 11 (the surface facing the vehicle cabin 13 side and Fig. 22 , 23 Towards the right and Fig.24 In the wide surface mainly shown in the figure, the area occupied by the soundproofing structural part 9 is preferably not less than 5% and not more than 95% of the area of ​​the entire soundproofing structure 11, and more preferably not less than 10% and not more than 40%, and further preferably not less than 20% and not more than 30%. If the proportion of the area occupied by the soundproofing structural part 9 is too small, the soundproofing property of the soundproofing structure 11, which is equivalent to the front panel silencer, becomes insufficient. In addition, if the proportion of the area occupied by the soundproofing structural part 9 is too large, there is the following disadvantage: the noise that passes through the soundproofing structure 11 and is transmitted to the vehicle compartment side is reflected on the instrument panel, and when it hits the surface of the soundproofing structure 11 on which the sound-absorbing material is not laminated and is reflected again, the sound pressure increases, generating a booming sound. Figures 22 to 25 In the example shown, the area occupied by the soundproofing structure 9 is approximately 30% of the entire area of ​​the soundproofing structure 11 .

[0216] In this example, the soundproof plate-like portion 10 and the soundproofing structure portion 9 are integrated. Specifically, the layer of soundproofing material (felt, polyurethane, glass wool, etc.) or the layer of soundproofing material (resin film, rubber sheet, etc.) constituting the soundproof plate-like portion 10 and at least one of the membrane portion 2 and the supporting wall portion 3 of the soundproofing structure portion 9 are integrally formed by insert molding, etc., or are mutually joined by any one of ultrasonic welding, bonding based on hot melt adhesive, and fixing based on clips, bolts, and rivets. Thus, the soundproofing structure 11 composed of the soundproof plate-like portion 10 and the soundproofing structure portion 9 can be easily handled.

[0217] The soundproof structure 11 of the present invention is not only the soundproof plate-shaped portion 10, but also the soundproof structure portion 9 as described above is very thin and light, and can be easily placed on a curved or uneven surface, so it is suitable for being placed on a passenger vehicle, especially a panel of a car (for example, Figure 1A-1B The panel 14 is used. The panel on which the soundproof structure 11 is mounted can be the same as the panel on which the soundproofing structures 1 and 6 are mounted. The configuration method, position, and usage form of the soundproofing structure 11 can be the same as the configuration method, position, and usage form of the soundproofing structures 1 and 6.

[0218] Furthermore, the soundproof structure 11 of the present invention has a soundproof structure portion 9 having the same structure as the soundproof structures 1 and 6 illustrated in the above-mentioned embodiments 1 to 14, and in addition, it is provided with a soundproof plate-like portion 10. Therefore, it can be said that the difference in the soundproofing properties of the soundproofing structures 1 and 6 of the embodiments 1 to 14 represents the difference in the soundproofing properties of each soundproofing structure 11. In addition, as described above, the soundproofing structures 1 and 6 of the embodiments 1 to 14 have greater soundproofing properties than the structures of the comparative examples 1 to 6, and on this basis, it can be considered that the soundproofing structure 11 of the present invention exhibits a more excellent soundproofing property to the extent that it is provided with the soundproof plate-like portion 10.

[0219] The present invention includes the following structures and methods.

[0220] [1] A sound insulation structure, characterized in that:

[0221] The invention comprises: an elastic membrane portion; an elastic supporting wall portion erected on the membrane portion; and a weight portion erected on the membrane portion.

[0222] The membrane portion is divided into a plurality of partitions by the support wall portion, the counterweight portion is located inside all of the plurality of partitions or inside a portion of the plurality of partitions, and one counterweight portion is arranged in one of the partitions where the counterweight portion is located.

[0223] The height of the support wall portion extending in the direction perpendicular to the membrane portion is greater than the height of the weight portion extending in the direction perpendicular to the membrane portion.

[0224] The weight portions each constitute a spring mass resonator including a spring portion having elasticity and a mass portion having a mass greater than that of the spring portion.

[0225] [2] A sound insulation structure according to [1], wherein:

[0226] The membrane portion, the support wall portion, and the spring portion are each made of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0227] [3] The sound insulation structure according to [1] or [2], wherein:

[0228] The diaphragm portion, the support wall portion, and the spring portion each have a dynamic storage modulus of 0.01 MPa to 100 MPa at 23° C. and a frequency of 1 Hz to 1000 Hz.

[0229] [4] The sound insulation structure according to any one of [1] to [3], wherein:

[0230] The diaphragm portion, the support wall portion, and the spring portion all have loss tangents of 0.01 or more and 0.50 or less at 23° C. and a frequency of 1 Hz to 1000 Hz.

[0231] [5] The sound insulation structure according to any one of [1] to [4], wherein:

[0232] The spring portion of the weight portion is located at a side where the weight portion is mounted on the diaphragm portion, and the mass portion is located at a side opposite to a side where the weight portion is mounted on the diaphragm portion.

[0233] [6] The sound insulation structure according to any one of [1] to [5], wherein:

[0234] The mass portion of the weight portion has a volume greater than a volume of the spring portion.

[0235] [7] The sound insulation structure according to any one of [1] to [6], wherein:

[0236] The mass portion of the weight portion is formed of a material having a density greater than that of the spring portion.

[0237] [8] A sound insulation structure, characterized in that:

[0238] The invention comprises: an elastic membrane portion; an elastic supporting wall portion erected on the membrane portion; and a weight portion erected on the membrane portion.

[0239] The membrane portion is divided into a plurality of partitions by the support wall portion, the counterweight portion is located inside all of the plurality of partitions or inside a portion of the plurality of partitions, and one counterweight portion is arranged in one of the partitions where the counterweight portion is located.

[0240] The height of the support wall portion extending in the direction perpendicular to the membrane portion is greater than the height of the weight portion extending in the direction perpendicular to the membrane portion.

[0241] The diaphragm portion serves as a spring portion, and the weight portion serves as a mass portion, thereby constituting a spring-mass resonator.

[0242] [9] A sound insulation structure according to [8], wherein:

[0243] The membrane portion and the support wall portion are each made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0244]

[10] The sound insulation structure according to [8] or [9], wherein:

[0245] The dynamic storage modulus of the membrane portion and the supporting wall portion at 23° C. and a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less.

[0246]

[11] The sound insulation structure according to any one of [8] to

[10] , wherein:

[0247] The loss tangent of the membrane portion and the support wall portion at 23° C. and a frequency of 1 Hz to 1000 Hz is 0.01 or more and 0.50 or less.

[0248]

[12] The sound insulation structure according to any one of [1] to

[11] , wherein:

[0249] The supporting wall portion includes: a plurality of first wall portions extending in a direction perpendicular to the membrane portion and in a first direction parallel to the membrane portion; and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and in a second direction perpendicular to the first direction.

[0250]

[13] The sound insulation structure according to any one of [1] to

[11] , wherein:

[0251] The support wall portion is in a cylindrical shape having a circular, elliptical or oblong cross-sectional shape that divides each of the divided areas, or in a square cylindrical shape having a polygonal cross-sectional shape that divides each of the divided areas.

[0252]

[14] The sound insulation structure according to any one of [1] to

[13] , wherein:

[0253] The area of ​​each of the above-mentioned zones is 100 mm 2 Above and 1000mm 2 the following.

[0254]

[15] The sound insulation structure according to any one of [1] to

[14] , wherein:

[0255] Each 1000cm of the above membrane 2 The area has 10 or more and 1,000 or less of the above-mentioned divisions.

[0256]

[16] A sound insulation structure according to

[15] , wherein:

[0257] Each 1000cm of the above membrane 2 The area has 50 or more and 500 or less of the above-mentioned divisions.

[0258]

[17] The sound insulation structure according to any one of [1] to

[16] , wherein:

[0259] The support wall portion has a plate thickness of 0.5 mm or more and 5.0 mm or less.

[0260]

[18] A sound insulation structure according to

[17] , wherein:

[0261] The support wall portion has a plate thickness of 1.0 mm or more and 3.0 mm or less.

[0262]

[19] The sound insulation structure according to any one of [1] to

[18] , wherein:

[0263] The film thickness of the film portion is greater than or equal to 0.1 mm and less than or equal to 3.0 mm.

[0264]

[20] The sound insulation structure according to any one of [1] to

[19] , wherein:

[0265] The height in the direction perpendicular to the film portion is 5 mm or more and 20 mm or less.

[0266]

[21] The sound insulation structure according to any one of [1] to

[20] , wherein:

[0267] A height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than or equal to 5 mm and less than or equal to 20 mm.

[0268]

[22] A sound insulation structure according to

[21] , wherein:

[0269] A height of the support wall portion extending in a direction perpendicular to the membrane portion is not less than 10 mm and not more than 20 mm.

[0270]

[23] The sound insulation structure according to any one of [1] to

[22] , wherein:

[0271] There are a plurality of the above-mentioned supporting walls,

[0272] A height of a part of the support wall portions extending in a direction perpendicular to the membrane portion is higher than a height of the other support wall portions.

[0273]

[24] A sound insulation structure according to

[23] , wherein:

[0274] The height of the relatively high support wall portion extending in a direction perpendicular to the membrane portion is greater than 10 mm and is 20 mm or less, and the height of the other support wall portions is 10 mm or less.

[0275]

[25] The sound insulation structure according to any one of [1] to

[24] , wherein:

[0276] The weight portion has a height of 1 mm or more extending in a direction perpendicular to the diaphragm portion.

[0277]

[26] The sound insulation structure according to any one of [1] to

[25] , wherein:

[0278] The membrane portion has a durometer A hardness of 30 or more, and the support wall portion has a durometer A hardness of 1 or more and 90 or less.

[0279]

[27] A soundproof structure, which is composed of a soundproof plate-like portion and a soundproofing structure portion, wherein:

[0280] The soundproof plate-shaped part is a plate-shaped component made of a sound absorbing material or a sound insulating material.

[0281] The sound insulation structure is composed of the sound insulation structure described in any one of [1] to

[26] .

[0282] At least one of the diaphragm portion and the support plate portion is formed integrally with the soundproof plate-shaped portion or is joined to each other, and the soundproof plate-shaped portion and the soundproof structure portion are arranged side by side on a plane.

[0283]

[28] The soundproofing structure according to

[27] , wherein:

[0284] The area occupied by the soundproofing structure on the main surface of the soundproofing structure is not less than 5% and not more than 95% of the area of ​​the entire soundproofing structure.

[0285]

[29] The soundproofing structure according to

[27] or

[28] , wherein:

[0286] At least one of the membrane portion and the support plate portion and the soundproof plate-like portion are formed integrally by insert molding, or are joined to each other by any one of ultrasonic welding, bonding with hot melt adhesive, and fixing with clips, bolts, and rivets.

[0287]

[30] The soundproofing structure according to any one of

[27] to

[29] , wherein:

[0288] The soundproof plate-like portion has a single-layer structure including either a layer made of felt, polyurethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are stacked.

[0289]

[31] The soundproofing structure according to any one of

[27] to

[30] , wherein:

[0290] A panel installed inside a car.

[0291]

[32] A soundproofing structure according to

[31] , wherein:

[0292] The sound insulation structure is mounted on a dashboard panel of an automobile and is provided at a position facing the tires.

[0293] Explanation of symbols

[0294] 1, 6—sound insulation structure, 2—diaphragm portion, 3—support wall portion, 3a—first wall portion, 3b—second wall portion, 3c—support wall portion with lower height (other supporting wall portions), 3d—support wall portion with higher height (part of the supporting wall portion), 4, 7—weight portion, 4a—spring portion, 4b—mass portion, 5—division, 8—iron plate, 9—sound insulation structural portion, 10—soundproof plate-like portion, 11—soundproof structure, 12—engine compartment, 13—vehicle compartment, 14—panel (front dash panel).

Claims

1. A sound insulation structure, characterized in that: The invention comprises: an elastic membrane portion; an elastic supporting wall portion erected on the membrane portion; and a weight portion erected on the membrane portion. The membrane portion is divided into a plurality of partitions by the support wall portion, the counterweight portion is located inside all of the plurality of partitions or inside a portion of the plurality of partitions, and one counterweight portion is arranged in one of the partitions where the counterweight portion is located. The height of the support wall portion extending in the direction perpendicular to the membrane portion is greater than the height of the weight portion extending in the direction perpendicular to the membrane portion. The weight portions each constitute a spring mass resonator including a spring portion having elasticity and a mass portion having a mass greater than that of the spring portion.

2. The sound insulation structure according to claim 1, characterized in that: The membrane portion, the support wall portion, and the spring portion are each made of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

3. The sound insulation structure according to claim 1 or 2, characterized in that: The diaphragm portion, the support wall portion, and the spring portion each have a dynamic storage modulus of 0.01 MPa to 100 MPa at 23° C. and a frequency of 1 Hz to 1000 Hz.

4. The sound insulation structure according to claim 3, characterized in that: The diaphragm portion, the support wall portion, and the spring portion all have loss tangents of 0.01 or more and 0.50 or less at 23° C. and a frequency of 1 Hz to 1000 Hz.

5. The sound insulation structure according to claim 1 or 2, characterized in that: The spring portion of the weight portion is located at a side where the weight portion is mounted on the diaphragm portion, and the mass portion is located at a side opposite to a side where the weight portion is mounted on the diaphragm portion.

6. The sound insulation structure according to claim 5, characterized in that: The mass portion of the weight portion has a volume greater than a volume of the spring portion.

7. The sound insulation structure according to claim 1 or 2, characterized in that: The mass portion of the weight portion is formed of a material having a density greater than that of the spring portion.

8. A sound insulation structure, characterized in that: The invention comprises: an elastic membrane portion; an elastic supporting wall portion erected on the membrane portion; and a weight portion erected on the membrane portion. The membrane portion is divided into a plurality of partitions by the support wall portion, the counterweight portion is located inside all of the plurality of partitions or inside a portion of the plurality of partitions, and one counterweight portion is arranged in one of the partitions where the counterweight portion is located. The height of the support wall portion extending in the direction perpendicular to the membrane portion is greater than the height of the weight portion extending in the direction perpendicular to the membrane portion. The diaphragm portion serves as a spring portion and the weight portion serves as a mass portion, thereby forming a spring mass resonator.

9. The sound insulation structure according to claim 8, characterized in that: The membrane portion and the support wall portion are each made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

10. The sound insulation structure according to claim 8 or 9, characterized in that: The dynamic storage modulus of the membrane portion and the supporting wall portion at 23° C. and a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less.

11. The sound insulation structure according to claim 10, characterized in that: The loss tangent of the membrane portion and the support wall portion at 23° C. and a frequency of 1 Hz to 1000 Hz is 0.01 or more and 0.50 or less.

12. The sound insulation structure according to claim 1 or 8, characterized in that: The supporting wall portion includes: a plurality of first wall portions extending in a direction perpendicular to the membrane portion and in a first direction parallel to the membrane portion; and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and in a second direction perpendicular to the first direction.

13. The sound insulation structure according to claim 1 or 8, characterized in that: The support wall portion is in a cylindrical shape having a circular, elliptical or oblong cross-sectional shape that divides each of the divided areas, or in a square cylindrical shape having a polygonal cross-sectional shape that divides each of the divided areas.

14. The sound insulation structure according to claim 1 or 8, characterized in that: The area of ​​each of the above divisions is 100mm 2 Above and 1000mm 2 the following.

15. The sound insulation structure according to claim 1 or 8, characterized in that: Each 1000cm of the above membrane 2 The area has 10 or more and 1,000 or less of the above-mentioned divisions.

16. The sound insulation structure according to claim 15, characterized in that: Each 1000cm of the above membrane 2 The area has 50 or more and 500 or less of the above-mentioned divisions.

17. The sound insulation structure according to claim 1 or 8, characterized in that: The support wall portion has a plate thickness of 0.5 mm or more and 5.0 mm or less.

18. The sound insulation structure according to claim 17, characterized in that: The support wall portion has a plate thickness of 1.0 mm or more and 3.0 mm or less.

19. The sound insulation structure according to claim 1 or 8, characterized in that: The film thickness of the film portion is greater than or equal to 0.1 mm and less than or equal to 3.0 mm.

20. The sound insulation structure according to claim 1 or 8, characterized in that: The height in the direction perpendicular to the film portion is 5 mm or more and 20 mm or less.

21. The sound insulation structure according to claim 1 or 8, characterized in that: A height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than or equal to 5 mm and less than or equal to 20 mm.

22. The sound insulation structure according to claim 21, characterized in that: A height of the support wall portion extending in a direction perpendicular to the membrane portion is not less than 10 mm and not more than 20 mm.

23. The sound insulation structure according to claim 1 or 8, characterized in that: There are a plurality of the above-mentioned supporting walls, A height of a part of the support wall portions extending in a direction perpendicular to the membrane portion is higher than a height of the other support wall portions.

24. The sound insulation structure according to claim 23, characterized in that: The height of the relatively high support wall portion extending in a direction perpendicular to the membrane portion is greater than 10 mm and is 20 mm or less, and the height of the other support wall portions is 10 mm or less.

25. The sound insulation structure according to claim 1 or 8, characterized in that: The weight portion has a height of 1 mm or more extending in a direction perpendicular to the diaphragm portion.

26. The sound insulation structure according to claim 1 or 8, characterized in that: The membrane portion has a durometer A hardness of 30 or more, and the support wall portion has a durometer A hardness of 1 or more and 90 or less.

27. A soundproof structure, comprising a soundproof plate-shaped portion and a soundproofing structural portion, wherein: The soundproof plate-shaped part is a plate-shaped component made of a sound absorbing material or a sound insulating material. The sound insulation structure is composed of the sound insulation structure according to claim 1. At least one of the diaphragm portion and the support plate portion is formed integrally with the soundproof plate-shaped portion or is joined to each other, and the soundproof plate-shaped portion and the soundproof structure portion are arranged side by side on a plane.

28. A soundproof structure, comprising a soundproof plate-shaped portion and a soundproofing structure, wherein: The soundproof plate-shaped part is a plate-shaped component made of a sound absorbing material or a sound insulating material. The sound insulation structure is composed of the sound insulation structure according to claim 8. At least one of the diaphragm portion and the support plate portion is formed integrally with the soundproof plate-shaped portion or is joined to each other, and the soundproof plate-shaped portion and the soundproof structure portion are arranged side by side on a plane.

29. The soundproof structure according to claim 27 or 28, characterized in that: The area occupied by the soundproofing structure on the main surface of the soundproofing structure is not less than 5% and not more than 95% of the area of ​​the entire soundproofing structure.

30. The soundproof structure according to claim 27 or 28, characterized in that: At least one of the membrane portion and the support plate portion and the soundproof plate-like portion are formed integrally by insert molding, or are joined to each other by any one of ultrasonic welding, bonding with hot melt adhesive, and fixing with clips, bolts, and rivets.

31. The soundproof structure according to claim 27 or 28, characterized in that: The soundproof plate-like portion has a single-layer structure including either a layer made of felt, polyurethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are stacked.

32. The soundproof structure according to claim 27 or 28, characterized in that: A panel installed inside a car.

33. The soundproof structure according to claim 32, characterized in that: The sound insulation structure is mounted on a dashboard panel of an automobile and is provided at a position facing the tires.

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