Sound insulation and soundproofing structures

Abstract

A sound insulation structure 1 has a film part 2 having elasticity, a support wall part 3 provided to stand on the film part 2 and having elasticity, and weight parts 4 provided to stand on the film part 2. The film part 2 is divided into a plurality of sections 5 by the support wall part 3, the weight parts 4 are respectively located within all of the plurality of sections 5 or within some sections 5 among the plurality of sections 5, and in the sections 5 within which the weight parts 4 are located, one weight part 4 is disposed in one section 5. The height H1 extending in a direction orthogonal to the film part 2 of the support wall part 3 is larger than the height H2 extending in the direction orthogonal to the film part 2 of the weight part 4. Each of the weight parts 4 constitutes a spring-mass resonator having a spring part 4a having elasticity and a mass part 4b having a larger mass than the spring part 4a. The sound insulation structure 1 can obtain sufficient sound insulation performance and be easily and stably mounted even on a curved mounting surface, and is thin and lightweight. A soundproof structure 11 comprises a soundproof plate-shaped part 10 and a sound insulation structure part 9 comprising the sound insulation structure 1. The film part 2 and / or the support plate part 3 and the soundproof plate-shaped part 10 are integrally formed or joined, and the soundproof plate-shaped part 10 and the sound insulation structure part 9 are located side by side in plan view.

Description

[Technical field]

[0001] The present invention relates to a sound insulating structure and a sound proof structure. [Background technology]

[0002] In recent years, in the rooms of buildings such as apartment buildings, office buildings, and hotels, outdoor noise from automobiles, trains, airplanes, ships, etc. outside the building, and equipment noise and human voices generated outside the room inside the building are required to be blocked, and quietness suitable for the use of the room is required. In addition, in the interior of vehicles such as automobiles, trains, airplanes, and ships, it is desired to reduce noise in order to block wind noise and engine noise and provide a quiet and comfortable space for the occupants. Therefore, there is a demand for means for blocking the propagation of noise and vibration from the outside to the inside of a building or vehicle, and also for the propagation of noise and vibration from the outside to the inside of a building or vehicle, that is, a member with high soundproofing properties. In recent years, there is a demand for lightweight soundproofing members in buildings due to the increase in height, and there is also a demand for lightweight soundproofing members in vehicles to improve energy efficiency. Examples of soundproofing structures forming soundproof walls in vehicles and buildings are disclosed in Patent Documents 1 to 6.

[0003] Patent Documents 1 and 2 disclose dash silencers (also called dash insulators) for automobiles. These dash silencers are laminated on a dash panel (dashboard) located at the boundary between the engine room and the passenger compartment, and suppress the intrusion of noise from the engine room into the passenger compartment. The dash silencer has a single-layer structure or a multi-layer structure that includes felt or urethane foam as a sound-absorbing material.

[0004] The invention described in Patent Document 3 relates to an acoustic damping panel comprising a rigid frame divided into a number of individual cells, a sheet of flexible material, and a number of weights, each weight being fixed to the sheet of flexible material such that each cell is provided with its own weight, and the attenuated sound is controlled by appropriate selection of the mass of the weights.

[0005] In the invention described in Patent Document 4, in a soundproofing material having an elastic sheet and a support part that holds the sheet and divides the sheet into partitions, the relationship between the rigidity of the sheet in the partitions and the areal density of the sheet is specified.

[0006] The soundproofing material of the invention described in Patent Document 5 is a structure comprising a flat substrate portion and a plurality of resonating portions connected to the substrate portion and having a predetermined resonant frequency, each of the plurality of resonating portions having a weight portion and a connecting portion connecting the weight portion to the substrate portion, and configured such that in a projection view viewed from a direction perpendicular to the substrate portion, the center of gravity of the resonating portion is located outside the joint area between the substrate portion and the connecting portion.

[0007] The vibration reduction device of the invention described in Patent Document 6 has an acoustic meta-structure that is attached to the vehicle body and blocks vibrations transmitted through the vehicle body, and includes a cross-shaped frame that is attached to the vehicle body and divides a certain space into certain areas, and vibrators that are configured at the corners of each area divided by the frame and have their own natural frequencies to block vibrations transmitted from the vehicle body through the frame. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] JP 2007-210381 A [Patent Document 2] JP 2018-012353 A [Patent Document 3] JP 2005-250474 A [Patent Document 4] International Publication No. WO2019 / 022245 [Patent Document 5] JP 2021-152584 A [Patent Document 6] JP 2020-91481 A Summary of the Invention [Problem to be solved by the invention]

[0009] The dash silencers described in Patent Documents 1 and 2 are unable to sufficiently reduce the noise entering the vehicle cabin. In particular, road noise transmitted from the ground into the vehicle cabin is large, and there is a risk that a quiet and comfortable space cannot be provided for the occupants.

[0010] The sound-damping panel described in Patent Document 3 has a rigid frame that is not flexible, and vibrations are transmitted to the seat via this rigid frame, so there is a risk that sufficient sound insulation cannot be obtained. In addition, if the support surface on which the rigid frame is placed is curved or uneven, the sound-damping panel may not be stably held. In particular, since the panels of general vehicles (e.g., automobiles) have many curved or uneven parts, it is difficult to simply use the sound-damping panel of Patent Document 3 as a sound-insulating material for vehicles. In addition, the rigid frame has a large mass, and the increase in mass due to the sound-insulating material in the vehicle may be a problem.

[0011] The soundproofing material described in Patent Document 4 has a high support part, i.e., a high height extending from the seat in a direction perpendicular to the seat, and is preferably 25 mm or more. In order to stably support the seat with such a high support part, it is preferable that the support part has rigidity. As a result, there is a risk that sufficient sound insulation cannot be obtained because vibrations are transmitted through the support part, and it is difficult to place the soundproofing material on a curved or uneven placement surface such as a panel of a vehicle (e.g., an automobile). In addition, such a high support part leads to an increase in size and weight of the entire soundproofing material, and when placed on a panel of a vehicle, the soundproofing material occupies a large space inside the vehicle, reducing space efficiency, and there is a concern that it will hinder the installation of other components and get in the way of passengers.

[0012] In the sound insulation material described in Patent Document 5, the resonating part, which is the functional part that exerts the sound insulation effect, is exposed and not covered by a supporting wall, etc., and there is a risk that the sound insulation performance will decrease or change if this resonating part comes into contact with other members or the human body. Therefore, it is necessary to provide a large space around the resonating part, which reduces the space efficiency.

[0013] The vibration reduction device described in Patent Document 6 does not have a membrane part, but is composed of a plurality of vibrators and a frame connecting them. Therefore, like the sound insulation material of Patent Document 5, the vibrator, which is a functional part that exerts a sound insulation effect, is exposed, and if this vibrator comes into contact with other members or the human body, 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, since vibration is transmitted through the frame, there is a risk that sufficient sound insulation cannot be obtained, and it is difficult to place the vibration reduction device of Patent Document 6 on a curved or uneven mounting surface such as a panel of a vehicle (e.g., an automobile).

[0014] Therefore, an object of the present invention is to provide a thin and lightweight soundproofing structure that can provide sufficient soundproofing properties and can be easily and stably placed on curved or uneven surfaces such as the panels of buildings, mechanical devices, and vehicles (e.g., automobiles), and that has good soundproofing properties, particularly in the low-frequency range of 1000 Hz or less, and a soundproofing structure including the soundproofing structure. [Means for solving the problem]

[0015] The first sound-proofing structure of the present invention comprises an elastic membrane portion, an elastic supporting wall portion standing on the membrane portion, and a weight portion standing on the membrane portion, the membrane portion being divided into a plurality of compartments by the supporting wall portion, the weight portion being located inside all of the plurality of compartments or inside some of the plurality of compartments, each weight portion being disposed in one of the compartments in which the weight portion is located, the height of the supporting wall portion extending in a direction perpendicular to the membrane portion being greater than the height of the weight portion extending in a direction perpendicular to the membrane portion, and each of the weight portions constituting a spring mass resonator having an elastic spring portion and a mass portion having a mass greater than that of the spring portion. The term "elasticity" used here refers to the property of a solid substance that has been deformed by an external force returning to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, a substance is said to have "elasticity" when it has at least one of energy elasticity and rubber elasticity (entropy elasticity). The support wall and the spring may be made of any 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 may be made of any 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. The film portion, the supporting 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 at a frequency of 1 Hz to 1000 Hz. The film portion, the supporting wall portion, and the spring portion may all be made of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. Specifically, the elasticity of the film part, the supporting wall part, and the spring part is evaluated by a dynamic storage modulus (E') obtained by measuring frequency dependency in tension or compression mode with a dynamic viscoelasticity measuring device in accordance with JIS K7244 and obtaining a master curve based on 23° C., and the dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less. More preferably, both the film part and the supporting wall part may be made of an elastic body having a dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 MPa or more and 50 MPa or less, and a loss tangent at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 or more and 0.45 or less. The spring portion of the weight may be located on a side of the weight that is attached to the membrane portion, and the mass portion may be located on a side of the weight that is opposite to the side that is attached to the membrane portion. The mass portion of the weight portion may have a larger volume than the spring portion. The mass portion of the weight portion may be made of a material having a higher density than the spring portion.

[0017] The support wall portion may include a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending 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 extending in a second direction perpendicular to the first direction. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 It may be the following: The area of ​​the membrane is 1000 cm 2 There may be from 10 to 1000 such compartments per unit area, and more preferably from 50 to 500 such compartments per unit area. The support wall portion may be cylindrical having a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or may be rectangular tubular having a polygonal cross-sectional shape that defines each of the compartments, specifically a square, regular pentagon or regular hexagon. The plate thickness of the support wall portion may be 0.5 mm or more and 5.0 mm or less, and is more preferably 1.0 mm or more and 3.0 mm or less. The film thickness of the film portion may be 0.1 mm or more and 3.0 mm or less. The height in a direction perpendicular to the film portion may be 5 mm or more and 20 mm or less. The height of the support wall in the direction perpendicular to the membrane may be 5 mm to 20 mm, and more preferably 10 mm to 20 mm. The support wall may have different heights in parts. The support wall may have a plurality of support walls, and some of the support walls may have a height extending in a direction perpendicular to the membrane portion greater than the other support walls. The height of the support wall that is taller extending in a direction perpendicular to the membrane portion may be greater than 10 mm and not greater than 20 mm, and the height of the other support walls (the support wall that is shorter) may be not greater than 10 mm. The support wall that is taller here refers to a support wall that is taller (for example, 1 mm or more) than the other support walls (the support wall that is shorter). The weight portion may have a height of 1 mm or more extending in a direction perpendicular to the film portion. The film portion may have a durometer A hardness of 30 or more, and the support wall portion may have a durometer A hardness of 1 or more and 90 or less. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3.

[0018] The first soundproof structure of the present invention is a soundproof structure comprising a soundproof plate-shaped portion and a soundproof structural portion, the soundproof plate-shaped portion being a plate-shaped member made of a sound-absorbing or sound-insulating material, the soundproof structural portion being made of the first soundproof structure described above, and the membrane portion and the support wall part At least one of the above and the soundproof plate-shaped portion is integrally formed or joined to each other, and the soundproof plate-shaped portion and the sound insulating structure portion are positioned side by side in a plane. The first soundproof structure may have the following configuration. The membrane portion, the support wall portion and the spring portion may all be made of a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity. 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. 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. Specifically, the elasticity of the membrane part, the supporting wall part, and the spring part is evaluated by measuring the frequency dependency in tension or compression mode with a dynamic viscoelasticity measuring device in accordance with JIS K7244, and obtaining a master curve based on 23°C, and the dynamic storage elastic modulus (E') at 23°C and at a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less. and spring part Each of these 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. The spring portion may be located on a side of the weight portion that is attached to the membrane portion, and the mass portion may be located on a side of the weight portion opposite to the side that is attached to the membrane portion. The mass portion may have a larger volume than the spring portion. The mass portion may be made of a material having a higher density than the spring portion.

[0020] Soundproofing structure The configuration may be as follows: On a main surface of the soundproof structure, an area occupied by the soundproof structural portion may be 5% to 95% of an area of ​​the entire soundproof structure. The support wall portion may include a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending 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 extending in a second direction perpendicular to the first direction. The support wall portion may be cylindrical having a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or may be rectangular tubular having a polygonal cross-sectional shape that defines each of the compartments, specifically a square, regular pentagon or regular hexagon. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 It may be the following: The area of ​​the membrane is 1000 cm 2 More preferably, the membrane portion has an area of ​​1000 cm or more and 1000 or less of the above-mentioned compartments. 2 There may be between 50 and 500 of said compartments per unit area. The support wall may have a thickness of 0.5 mm or more and 5.0 mm or less. More preferably, the support wall may have a thickness of 1.0 mm or more and 3.0 mm or less. The membrane may have a thickness of 0.1 mm or more and 3.0 mm or less. The height in a direction perpendicular to the film portion may be 5 mm or more and 20 mm or less. The height of the support wall portion extending in a direction perpendicular to the membrane portion may be 5 mm or more and 20 mm or less, and the height may vary partially. The weight portion may have a height of 1 mm or more extending in a direction perpendicular to the film portion. The film portion may have a durometer A hardness of 30 or more, and the support wall portion may have a durometer A hardness of 1 or more and 90 or less. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3. The membrane portion and the support wall partAt least one of the above and the soundproof plate-like portion may be integrally formed by insert molding, or may be joined to each other by ultrasonic welding, bonding with an adhesive, bonding with an adhesive tape, or fixing with a clip, bolt, staple, or rivet. The soundproof plate-like portion or the soundproof structure portion may be shaped in such a way that the soundproof structure portion and the soundproof plate-like portion are joined to each other. For example, the soundproof plate-like portion may have a fitting hole, and the soundproof structure portion and the soundproof plate-like portion may be joined to each other by simply fitting a part of the film portion into the fitting hole. The soundproof plate-like portion may have a single-layer structure consisting of either a layer made of felt, urethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are laminated. The sound insulation structure may be attached to an interior panel of the automobile, or may be attached to a dash panel of the automobile, and each of the sound insulation structures may be provided at a position facing the tire. Effect of the Invention

[0021] According to the present invention, it is possible to provide a thin and lightweight soundproofing structure that has sufficient soundproofing properties and can be easily and stably placed on a curved or uneven support surface such as the panel of a building, mechanical device, or vehicle (e.g., an automobile), and that has particularly good soundproofing properties in the low-frequency range of 1000 Hz or less, and a soundproofing structure including the same. [Brief description of the drawings]

[0022] [Figure 1A] 1 is a perspective view of a sound insulation structure according to a first embodiment of the present invention. [Figure 1B] FIG. 1B is a cross-sectional view taken along line AA in FIG. 1A. [Figure 2A] FIG. 2 is an exploded perspective view of one section of the sound insulation structure shown in FIGS. 1A and 1B. [Figure 2B] FIG. 2 is an exploded front view of one section of the sound-insulating structure shown in FIGS. 1A and 1B. [Figure 3A] FIG. 2 is a perspective view of a sound insulation structure according to a modified example of the first embodiment of the present invention. [Figure 3B] 3B is a cross-sectional view taken along line AA in FIG. 3A. [Figure 4A] FIG. 4 is a cross-sectional view of a sound insulation structure according to another modified example of the first embodiment of the present invention. [Figure 4B] 4B is a perspective view of a weight portion of the sound-proofing structure shown in FIG. 4A. [Figure 5A] FIG. 11 is a cross-sectional view of a sound insulation structure according to still another modified example of the first embodiment of the present invention. [Figure 5B] 5B is a perspective view of a weight portion of the sound-proofing structure shown in FIG. 5A. [Figure 6A] FIG. 4 is a perspective view of a sound insulation structure according to a second embodiment of the present invention. [Figure 6B] 6B is a cross-sectional view taken along line AA in FIG. 6A. [Figure 7A] FIG. 11 is a cross-sectional view of a sound insulation structure according to a modified example of the second embodiment of the present invention. [Figure 7B] 7B is a perspective view of a weight portion of the sound-proofing structure shown in FIG. 7A. [Figure 8A] FIG. 2 is a plan view showing a schematic view of one section of the sound-insulating structure of the present invention. [Figure 8B] FIG. 2 is a plan view showing a schematic view of a plurality of compartments of the sound insulation structure of the present invention. [Figure 9A] FIG. 4 is a plan view showing a schematic view of one section of another example of the sound-insulating structure of the present invention. [Figure 9B] FIG. 11 is a plan view showing a schematic view of a plurality of compartments of another example of a sound-insulating structure of the present invention. [Figure 10A] FIG. 11 is a plan view showing a schematic view of one section of still another example of a sound-insulating structure of the present invention. [Figure 10B] 13 is a plan view showing a schematic view of a plurality of compartments of still another example of a sound insulation structure of the present invention. FIG. [Figure 11A] FIG. 11 is a plan view showing a schematic view of one section of still another example of a sound-insulating structure of the present invention. [Figure 11B] 13 is a plan view showing a schematic view of a plurality of compartments of still another example of a sound insulation structure of the present invention. FIG. [Figure 12A] FIG. 11 is a plan view showing a schematic view of one section of still another example of a sound-insulating structure of the present invention. [Figure 12B] 13 is a plan view showing a schematic view of a plurality of compartments of still another example of a sound insulation structure of the present invention. FIG. [Figure 13] FIG. 2 is a cross-sectional view showing a state in which the sound-proofing structure of the first embodiment of the present invention is attached to an iron plate. [Figure 14A] 1 is a graph showing sound insulation properties of Example 1 of the present invention and Comparative Examples 1 to 3. [Figure 14B] 1 is a graph showing sound insulation properties of Examples 1 to 3 of the present invention and Comparative Example 3. [Figure 14C] 1 is a graph showing sound insulation properties of Examples 1 and 4 of the present invention and Comparative Example 4. [Figure 14D] 1 is a graph showing the sound insulation properties of Examples 1 and 5 of the present invention. [Figure 14E] 1 is a graph showing sound insulation properties of Examples 1 and 6 of the present invention. [Figure 14F] 1 is a graph showing sound insulation properties of Examples 1, 7, and 8 of the present invention and Comparative Example 3. [Figure 14G] 1 is a graph showing the sound insulation properties of Examples 8 and 9 of the present invention. [Figure 14H] 1 is a graph showing the sound insulation properties of Examples 9 and 10 of the present invention. [Figure 14I] 1 is a graph showing the sound insulation properties of Examples 9 and 11 of the present invention. [Figure 14J] 1 is a graph showing sound insulation properties of Examples 12 to 14 of the present invention and Comparative Example 5. [Figure 14K] 1 is a graph showing sound insulation properties of Example 1 of the present invention and Comparative Example 6. [Figure 15] FIG. 1 is a cross-sectional view of the structure of Comparative Example 1. [Figure 16A] FIG. 11 is a perspective view of a sound-insulating structure of Comparative Example 3. [Figure 16B] 16B is a cross-sectional view showing the sound-proof structure shown in FIG. 16A attached to an iron plate. [Figure 17] FIG. 11 is a cross-sectional view showing a state in which a sound-proofing structure according to a second embodiment of the present invention is attached to an iron plate. [Figure 18A] FIG. 11 is a perspective view of a sound insulation structure according to a third embodiment of the present invention. [Figure 18B]18B is a cross-sectional view showing the sound-proof structure shown in FIG. 18A attached to an iron plate. [Figure 19A] FIG. 11 is a perspective view of a sound insulation structure according to a sixth embodiment of the present invention. [Figure 19B] 19B is a cross-sectional view showing the sound-proof structure shown in FIG. 19A attached to an iron plate. [Figure 20] FIG. 13 is a cross-sectional view showing a state in which a sound-proofing structure according to a tenth embodiment of the present invention is attached to an iron plate. [Figure 21A] FIG. 23 is a perspective view of a sound insulation structure according to an eleventh embodiment of the present invention. [Figure 21B] 21B is a cross-sectional view showing the sound-proofing structure shown in FIG. 21A attached to an iron plate. [Figure 22] 1 is a side view of an automobile, which is an example of a vehicle provided with a soundproof structure of the present invention. [Diagram 23] FIG. 23 is a side view of the soundproof structure shown in FIG. 22. [Figure 24] 23 is a perspective view of the soundproof structure shown in FIG. 22 as viewed from the front side. [Diagram 25] 25 is a cross-sectional view taken along line CC in FIG. 24. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0023] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. [First embodiment] FIG. 1A is a perspective view of a sound insulation structure 1 according to a first embodiment of the present invention, and FIG. 1B is a cross-sectional view taken along line AA in FIG. 1A and turned upside down. The sound insulation structure 1 has an elastic sheet-like film portion 2, an elastic support wall portion 3 standing substantially vertically from the film portion 2, and a weight portion 4 standing substantially vertically from the film portion 2. The film portion 2 is divided into a plurality of sections (unit structures) 5 by the support wall portion 3. The weight portion 4 is located in each of all of the sections 5, or in some of the sections 5 among the plurality of sections 5. In the section 5 in which the weight portion 4 is located, one weight portion 4 is located in one section 5. FIG. 2A is an exploded perspective view of one section 5 of the sound insulation structure 1, and FIG. 2B is an exploded front view thereof. The height H1 of the support wall portion 3 extending from the film portion 2 in a direction perpendicular to the film portion 2 is greater than the height H2 of the weight portion 4 extending from the film portion 2 in a direction perpendicular to the film portion 2. Each of the weights 4 constitutes a spring-mass resonator having an elastic spring portion 4a and a mass portion (mass portion) 4b having a larger mass than the spring portion 4a. The term "elasticity" as used here refers to the property of a solid material that has been deformed by an external force returning to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, the term "having elasticity" refers to the case where at least one of energy elasticity and rubber elasticity (entropy elasticity) is present.

[0024] The support wall 3 of this embodiment includes a plurality of first walls 3a extending in a first direction D1 parallel to the membrane 2, and a plurality of second walls 3b extending in a second direction D2 perpendicular to the first direction D1. Specifically, the plurality of first walls 3a are arranged in parallel, and the plurality of second walls 3b are arranged in parallel, and the first walls 3a and the second walls 3b are integrated at the intersections. In this way, the plurality of first walls 3a and the plurality of second walls 3b form a lattice structure, and a plurality of compartments 5 having a square planar shape partitioned by the first walls 3a and the second walls 3b are arranged in a matrix shape. In other words, the support wall 3 has a structure in which a plurality of square tubes having a square cross-sectional shape that defines each compartment 5 are arranged. The support wall 3 is preferably made of a flexible material such as rubber, elastomer, or resin foam. The flexible material referred to here is any one of a material that has rubber elasticity but not energy elasticity, a material that has energy elasticity but not rubber elasticity, and a material that has both rubber elasticity and energy elasticity.

[0025] In this embodiment, the part of the weight part 4 attached to the membrane part 2 is the spring part 4a, and the part opposite to the side attached to the membrane part 2 is the mass part 4b, which has a larger mass than the spring part 4a. In the example shown in Figs. 1A to 2B, the spring part 4a and the mass part 4b have the same shape and the same dimensions, but are made of different materials. The spring part 4a is made of a flexible material, and the mass part 4b is made of a material with a higher density than the material constituting the spring part 4a. A spring mass resonator is configured in which the spring part 4a functions as a spring and the mass part 4b functions as a mass. In addition to the spring part 4a of the weight part 4, the membrane part 2 may also function as a part of the spring of the spring mass resonator. Furthermore, the air in the space surrounded by the membrane part 2 and the support wall part 3 may also function as a part of the spring of the spring mass resonator (air spring). Spring part 4a too It is preferable that the material be made of a flexible material, that is, a material that has rubber elasticity but not energy elasticity, a material that has energy elasticity but not rubber elasticity, or a material that has both rubber elasticity and energy elasticity.

[0026] According to the sound-proofing structure 1 of this embodiment, the vibration of the film portion 2 is controlled by the action of a spring-mass resonator constituted by the spring portion 4a and the mass portion 4b of the weight portion 4. In particular, in a specific frequency range (for example, frequencies below 1000 Hz, which is the main frequency band of road noise in automobiles), the film vibration is significantly reduced, and as a result, the sound radiated from the film portion 2 is reduced, and high sound insulation is achieved.

[0027] The section 5 of the sound insulation structure 1 of this embodiment has a membrane part 2 with an area of ​​1000 cm 2 It is preferable that 10 to 1000 sections are provided per unit area, and more preferably 50 to 500 sections are provided per unit area. If there are too few sections 5, the effect of dividing the entire sound insulation structure 1 into a plurality of sections 5 and having each section provide its own sound insulation effect is poor, and the sound insulation of the entire sound insulation structure 1 may be reduced. On the other hand, if there are too many sections 5, the weight of the entire sound insulation structure 1 may increase. The planar area of ​​each section 5 is 100 mm 2 More than 1000mm 2 It is preferable that the length is less than 200 mm. 2 More than 800mm 2 It is more preferable that the height is 5 mm or less. If the area of ​​the planar shape of each section 5 is too small, it may be difficult to arrange the weight section 4 inside, and if the area is too large, the effect of the weight section 4 on the film section 2 may be poor, and the sound insulation may be reduced. The height of the entire sound insulation structure 1 in the direction perpendicular to the film section 2 is preferably 5 mm or more and 20 mm or less. If the height of the entire sound insulation structure 1 is too low, the weight section 4 may not have a sufficient height as a spring mass resonator, and if it is too high, the weight of the entire sound insulation structure 1 may increase. Each drawing shows each section 5 and the support wall section 3, etc., and the number and area of ​​the sections 5 and the height of the sound insulation structure 1 may not be shown strictly and accurately, or may not be unified in each drawing, but it is preferable that the number and area of ​​the sections 5 and the height of the sound insulation structure 1 are appropriately designed to be within the above-mentioned numerical ranges.

[0028] The film portion 2, the supporting wall portion 3, and the spring portion 4a of the sound insulation structure 1 of this embodiment are all made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa to 100 MPa at 23° C. and a loss tangent (tan δ) of 0.01 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, preferably a dynamic storage modulus (E') of 0.05 MPa to 50 MPa at 23° C. and a loss tangent (tan δ) of 0.05 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, respectively. The dynamic storage modulus (E') and the loss tangent (tan δ) are determined by creating a master curve based on 23° C. using a dynamic viscoelasticity tester. If the dynamic storage modulus (E') at 23°C and frequencies of 1 Hz to 1000 Hz is less than 0.01 MPa, the sound insulation in the target frequency band may deteriorate, and the shape retention of the film part 2 and the supporting wall part 3 may also deteriorate. If the dynamic storage modulus (E') at 23°C and frequencies of 1 Hz to 1000 Hz is more than 100 MPa, the vibration in the frequency band to be sound-insulated may deteriorate, and the sound-insulating structure 1 may become rigid and the installation may deteriorate. The film part 2 and the supporting wall part 3 may be formed of the same material or different materials. It is preferable that the film part 2 is also made of a flexible 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, or a material that has both rubber elasticity and energy elasticity.

[0029] The film portion 2 is preferably a hard elastic film because the weight portion 4 is attached to it. The dynamic storage elastic modulus (E') of the film portion 2 is preferably 15 MPa or more, and the thickness (film thickness) is preferably 0.1 mm or more and 3.0 mm or less, and more preferably about 0.5 mm. If the thickness of the film portion 2 is less than 0.1 mm, the vibration of the film portion 2 may deteriorate, and the sound insulation of the frequency band to be sound-insulated may deteriorate, and if the thickness of the film portion 2 is more than 3.0 mm, the thickness and weight of the entire sound-insulating structure 1 may increase. The material of the film portion 2 preferably has a durometer A hardness of 30 or more according to JIS K6253, and more preferably 70 or more. If the durometer A hardness of the film portion 2 is less than 30, the vibration of the film portion 2 may deteriorate, and the sound insulation of the frequency band to be sound-insulated may deteriorate. The stiffness (axial stiffness) 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 stiffness is 1000 cm 2 When the stiffness k is 10 6 N / mm or more 10 9 N / mm or less is preferable, and 3×10 6 N / mm or more 10 8 It is more preferable that the surface area of ​​the membrane portion 2 is 1000 cm 2 When the stiffness is 10 6 If the surface area of ​​the film 2 is less than 1000 cm2, the vibration of the film 2 may deteriorate, and the sound insulation performance in the frequency band to be insulated may deteriorate. 2 When the stiffness is 10 9 If it is larger than N / mm, the sound insulation structure 1 becomes too rigid, and there is a risk that the installation may become difficult. The bending rigidity K of the film part 2 is expressed as K=E'×I from the dynamic storage elastic modulus E' and the second moment of area I, and the second moment of area I is expressed as I=b×h from the thickness h of the film part 2 and the width b of the film part 2. 3 / 12. When the area of ​​the membrane part 2 to be evaluated is 1000 cm 2 When the bending stiffness K is 30N / mm 2 Over 10 5 N / mm 2 It is preferable that the resistance is less than 50N / mm 2 5×10 or more4 N / mm 2 It is more preferable that the area of ​​the membrane portion 2 is 1000 cm or less. 2 The bending stiffness K when 2 If the area of ​​the film portion 2 is less than 1000 cm, the vibration of the film portion 2 may deteriorate, and the sound insulation performance in the frequency band to be insulated may deteriorate. 2 When the bending stiffness K is 10 5 N / mm 2 If it is larger, the sound insulation structure 1 becomes too rigid, which may deteriorate the ease of installation. The cross-sectional shape of the film portion 2 is not particularly limited, and may be flat or may have irregularities.

[0030] Examples of materials for the membrane portion 2 include crosslinked (vulcanized) rubber, thermoplastic elastomer, and plastic. Examples of crosslinked (vulcanized) rubber include natural rubber (NR), isoprene rubber (IR), butadiene rubber (BR), styrene-butadiene rubber (SBR), chloroprene rubber (CR), butyl rubber (IIR), nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), ethylene-α-olefin-non-conjugated polyene copolymers such as ethylene-propylene rubber (EPM), ethylene-propylene-diene rubber (EPDM) and ethylene-butene-diene rubber (EBDM), 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), silicone rubber (Q) such as methylvinylsilicone rubber (VMQ) and fluorinated silicone rubber (FVMQ), urethane rubber (U), and fluororubber (FKM). These crosslinked (vulcanized) rubbers can be used alone or in combination of two or more kinds. Examples of the crosslinking (vulcanization) method include a method of crosslinking (vulcanization) by heating using an organic peroxide, a phenolic resin, an oxime compound, sulfur, a sulfur-based compound, or a polyamine compound as a crosslinking agent (vulcanizing agent), or a method of crosslinking by irradiating with an electron beam. The crosslinked (vulcanized) rubber may contain various known compounding agents (reinforcing agents such as carbon black and silica, fillers such as calcium carbonate, softeners such as paraffin oil and plasticizers, processing aids, antioxidants, light stabilizers, flame retardants, antifungal agents, acid acceptors, silane coupling agents, antistatic agents, ultraviolet absorbing agents, etc.) that are generally used as rubber compounding agents. These crosslinked (vulcanized) rubbers, crosslinking agents (vulcanizing agents), and compounding agents may be made from biomass raw materials.

[0031] Examples of the thermoplastic elastomer 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. Examples of the plastic include polyethylene, polypropylene, polystyrene, polyethylene terephthalate, polyvinyl chloride, and composite resins containing these. These thermoplastic elastomers and plastics may be made from biomass raw materials.

[0032] Specifically, the material of the film portion 2 is preferably ethylene-propylene-diene rubber, a thermoplastic olefin-based elastomer, a thermoplastic styrene-based elastomer, polyethylene, polypropylene, polyethylene terephthalate, thermoplastic polyurethane, or the like.

[0033] The supporting wall 3 is preferably made of a soft, flexible material within a range capable of supporting the film 2. The plate thickness of the supporting wall 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. If the plate thickness of the supporting wall 3 is less than 0.5 mm, the shape retention of the sound insulation structure 1 may be deteriorated. If the plate thickness of the supporting wall 3 is more than 5.0 mm, the vibration of the film 2 may be deteriorated, the sound insulation of the frequency band to be sound-insulated may be deteriorated, and the weight of the entire sound insulation structure 1 may also be increased. The height of the supporting wall 3 extending in a direction perpendicular to the film 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 3 may have a different height in parts. When the height of the supporting wall 3 is different in parts, the higher part may be 10 mm or more and 20 mm or less, more preferably 12 mm or more and 20 mm or less, and even more preferably 14 mm or more and 20 mm or less. If the height of the supporting wall 3 is too low, the weight 4 may not have a sufficient height as a spring mass resonator. If the height of the supporting wall 3 is too high, the overall weight may increase. The material of the supporting wall 3 preferably has a durometer A hardness according to JIS K6253 of 1 to 90, more preferably 10 to 70. If the durometer A hardness of the supporting wall 3 is less than 1, the shape retention of the sound insulation structure 1 may deteriorate. If the durometer A hardness of the supporting wall 3 is greater than 90, vibration from the supporting wall 3 may be transmitted to the membrane 2, deteriorating the sound insulation performance, and the sound insulation structure 1 may become rigid and poor in installation. The rigidity k of the supporting wall 3 is expressed as k=E'×A / L, where E' is the dynamic storage elastic modulus, A is the cross-sectional area of ​​the supporting wall 3, and L is the height of the supporting wall 3. If the area of ​​the supporting wall 3 to be evaluated for rigidity is 1000 cm 2 When the stiffness k is 10N / mm or more, 6 It is preferable that the resistance is less than 10 N / mm. 2 N / mm or more 10 5 It is more preferable that the surface area of ​​the support wall 3 is 1000 cm or less. 2When the stiffness k is less than 10 N / mm, the shape retention of the sound insulation structure 1 may be deteriorated. 2 When the stiffness k is 10 6 If it is greater than N / mm, vibration from the supporting wall portion 3 will be transmitted to the film portion 2, resulting in a deterioration in sound insulation performance and also in the sound insulation structure 1 becoming too rigid, which may result in a deterioration in installability.

[0034] Examples of the material of the support wall 3 include crosslinked (vulcanized) rubber, thermoplastic elastomer, and resin foam. The crosslinked (vulcanized) rubber and thermoplastic elastomer may be the same as the materials listed as the materials of the membrane 2. The resin foam may have a closed cell structure or an open cell structure, and examples of the resin foam include polyurethane foam, polystyrene foam, polyethylene foam, and ethylene-vinyl acetate rubber (EVA) foam. Specifically, the material of the support wall 3 is preferably ethylene-propylene-diene rubber, urethane rubber, silicone rubber, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, thermoplastic polyurethane, and polyurethane foam. These resin foams may be made of biomass raw materials.

[0035] The material of the spring portion 4a of the weight portion 4 is a flexible material such as crosslinked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. The crosslinked (vulcanized) rubber, thermoplastic elastomer, and resin foam may be the same as the materials given as the materials 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, urethane rubber, silicone rubber, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, thermoplastic polyurethane, polyurethane foam, etc.

[0036] The material of the mass portion 4b is not particularly limited, but it is made of resin, metal, or the like, and the mass portion 4b has a larger mass than the spring portion 4a, for example, a mass of 0.1 g or more and 2.0 g or less. The mass portion 4b preferably has a mass at least twice the mass of the spring portion 4a. If the weight of the mass portion 4b is less than twice the mass of the spring portion 4a, the weight portion 4 cannot resonate sufficiently in the frequency range to be sound-insulated, and sound insulation may be deteriorated. When the material of the mass portion 4b is resin, the resin may be made of a biomass material.

[0037] 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 to be mainly sound-insulated. As an example, when the mass portion 4b has a mass of 1.0 g and the frequency to be mainly sound-insulated is 1000 Hz or less, the spring constant of the spring portion 4a is 1 N / mm or more and 50 N / mm or less.

[0038] With this configuration, the film portion 2, the support wall portion 3, and the weight portion 4 are all relatively light, and the dimensions in the direction perpendicular to the film portion 2 are relatively small. Thus, the sound-insulating structure 1 of this embodiment is lightweight and thin, yet provides high sound insulation in a specific frequency range (for example, 1000 Hz or less) as described above. Furthermore, the support wall portion 3 made of a flexible material can be easily and stably installed on a flat support surface as well as a curved or uneven support surface without being fixed by adhesive or the like.

[0039] FIG. 3A is a perspective view of a sound insulation structure 1 of a modification of the first embodiment of the present invention, and FIG. 3B is a cross-sectional view taken along line AA in FIG. 3A and inverted. FIG. 4A is a cross-sectional view of the sound insulation structure 1 of another modification, and FIG. 4B is a perspective view of the weight portion 4 of the sound insulation structure 1. FIG. 5A is a cross-sectional view of the sound insulation structure 1 of yet another modification, and FIG. 5B is a perspective view of the weight portion 4 of the sound insulation structure 1. In these modifications, the spring portion 4a and the mass portion 4b of the weight portion 4 have different shapes and different dimensions. In the modification shown in FIGS. 3A and 3B, the spring portion 4a is a small-diameter cylindrical portion, and the mass portion 4b is a large-diameter cylindrical portion. In the modification shown in FIGS. 4A and 4B, the spring portion 4a is an elongated cylindrical portion, the mass portion 4b is a spherical portion, 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. In the modified example shown in Figs. 5A and 5B, the spring portion 4a is truncated cone-shaped, the mass portion 4b is cylindrical, and the diameter of the smallest part of the truncated cone-shaped spring portion 4a is substantially equal to the diameter of the cylindrical mass portion 4b. In the modified example shown in Figs. 3A to 4B, 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 made of the same material, the mass portion 4b has a larger mass than the spring portion 4a, and a spring-mass resonator can be configured. However, in this modified example, the spring portion 4a and the mass portion 4b may be made of different materials, and the mass portion 4b may have a larger mass than the spring portion. On the other hand, in the modified example shown in Figs. 5A and 5B, the spring portion 4a has a larger volume than the mass portion 4b. In this case, the mass portion 4b is made of a material having a higher density than the spring portion 4a, and the mass portion 4b has a larger mass than the spring portion, and a spring-mass resonator can be configured. As in the modified example shown in Figures 5A and 5B, when the spring portion 4a has a truncated cone shape tapering in the direction away from the membrane portion 2, the membrane portion 2 and the spring portion 4a are easily releasable from a mold when they are molded integrally.

[0040] In this embodiment, the spring portion 4a and the mass portion 4b of the weight portion 4 are made different in either material or volume or both, so that the mass portion 4b has a larger mass than the spring portion 4a to configure a spring mass resonator and obtain a sufficient sound insulation effect. That is, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b are determined so that a spring mass resonator that can provide a sufficient sound insulation effect can be configured. As long as the mass of the mass portion 4b can be made larger than the spring portion 4a to the extent that a spring mass resonator that can provide a sufficient sound insulation effect can be configured in this way, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b can be freely selected. However, the spring portion 4a needs to be made of a flexible material in order to function as a spring.

[0041] [Second embodiment] FIG. 6A is a perspective view of a sound insulation structure 6 according to a second embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along line AA in FIG. 6A and turned upside down. The sound insulation structure 6 has a weight portion 7 of a single structure that is not divided into a spring portion and a mass portion. In this embodiment, a spring-mass resonator is configured in which the entire weight portion 7 functions as the mass portion and the film portion 2 functions as the spring portion. As an example, the mass of the weight portion 7 is about 0.1 g to 2.0 g. The material of the weight portion 7 is not limited, and it is formed from, for example, a synthetic resin or metal. The other configuration is the same as that of the first embodiment described above, so a description thereof will be omitted. In the sound insulation structure 6 of this embodiment, the membrane vibration is also controlled by the action of the spring-mass resonator formed by the weight portion 7 and the film portion 2, and the membrane vibration is significantly reduced in a specific frequency range (for example, 1000 Hz or less), thereby providing high sound insulation. In addition, together with the membrane portion 2, the air in the space surrounded by the membrane portion 2 and the support wall portion 3 may function as a part of the spring of the spring mass resonator (air spring).

[0042] In both the film part 2 and the supporting wall part 3 of this embodiment, it is preferable that the dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less, and the loss tangent (tan δ) at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.01 or more and 0.50 or less. Furthermore, it is more preferable that the dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.05 MPa or more and 50 MPa or less, and the loss tangent (tan δ) at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.05 or more and 0.50 or less.

[0043] The support wall 3 of this embodiment is 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 2 of this embodiment is 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.

[0044] Fig. 7A is a cross-sectional view of a sound insulation structure 6 according to a modification of the second embodiment of the present invention, and Fig. 7B is a perspective view of the weight 7 of the sound insulation structure 6. In this modification, the weight 7 has a truncated cone shape that tapers in the direction away from the film 2. With this configuration, the weight 7 can be easily releasable from a mold when the film 2 and the weight 7 are molded integrally. In this embodiment, the shape of the weight 7 can be determined arbitrarily and is not particularly limited.

[0045] In any of the first and second embodiments, the film portion 2 and the supporting wall portion 3 can be formed by integral molding or two-color molding using the above-mentioned materials by injection molding, compression molding, press molding, extrusion molding, transfer molding, casting, etc. Furthermore, the weight portions 4, 7 can also be formed by integral molding, two-color molding, insert molding, etc. together with the film portion 2 and the supporting wall portion 3 using the above-mentioned materials. However, the sound-insulating structures 1, 6 may be assembled by first forming the film portion 2, the supporting wall portion 3, and the weight portions 4, 7 separately, and then joining them together by adhesion or heat fusion.

[0046] In the configuration of the sound insulation structures 1 and 6 described above, as shown in Figs. 8A and 8B, the support wall 3 includes a plurality of first wall portions 3a extending in a first direction D1 parallel to the film portion 2 and a plurality of second wall portions 3b extending in a second direction D2 perpendicular to the first direction D1, and the planar shape of each section 5 is a square. In other words, the support wall portion 3 is a square tube having a square cross-sectional shape that defines each section 5, and a large number of square tube-shaped support walls 3 are arranged side by side, and the support walls 3 of adjacent sections 5 are integrated. However, the configuration is not limited to this. For example, as shown in Figs. 9A and 9B, the planar shape of each section 5 may be a triangle, and the support wall portion 3 may be a square tube having a triangular cross-sectional shape that defines each section 5. As shown in Figs. 10A and 10B, the planar shape of each section 5 may be pentagonal, and the support wall 3 may be a square tube having a pentagonal cross-sectional shape that defines each section 5. As shown in Figs. 11A and 11B, the planar shape of each section 5 may be hexagonal, and the support wall 3 may be a square tube having a hexagonal cross-sectional shape that defines each section 5, forming a so-called honeycomb structure. Furthermore, as shown in Figs. 12A and 12B, the planar shape of each section 5 may be circular, and the support wall 3 may be a cylinder having a circular cross-sectional shape that defines each section 5. In the case of the configuration shown in Figs. 10A, 10B, 12A, and 12B, gaps are generated between the sections 5, so it is preferable to determine the shape and dimensions of the support wall 3 so that the gaps are small. In the case of the configuration shown in Figs. 8A, 8B, 9A, 9B, 11A, and 11B, no gaps are generated between the sections 5. Furthermore, each compartment 5 may have various shapes (not shown), such as a rectangle, a parallelogram, a trapezoid, a polygon having seven or more sides, an ellipse, an oval, or an irregular shape. The support wall 3 is formed to have a shape and dimensions that match the planar shape of each compartment 5.

[0047] The sound insulation structures 1, 6 of the present invention are very thin and lightweight, and can be easily placed on a curved or uneven surface, so they may be placed on the panel of a vehicle, particularly an automobile, for use. The panel of an automobile or the like is basically a plate with no air permeability, and examples thereof include a metal plate (iron plate, steel plate, aluminum plate) and a resin plate. When 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 when it is a resin plate, its thickness is preferably in the range of 0.5 mm to 20 mm. When the sound insulation structures 1, 6 are placed on the panel of an automobile, it is preferable that the end face of the support wall portion 3 of the sound insulation structures 1, 6 opposite to the side attached to the film portion 2 is placed on the panel. In this case, the support wall portion 3 and the panel may or may not be bonded to each other, but it is preferable that the support wall portion 3 is placed on the panel without being bonded to the panel.

[0048] The sound insulation structure 1,6 of the present invention may be used alone or in combination with other members (not shown). When the sound insulation structure 1,6 of the present invention is used in combination with other members, it may be laminated or joined to the other members. When laminated or joined to other members, the sound insulation structure 1,6 may be placed so as to be in contact with the portion (e.g., an automobile panel) on which the sound insulation structure 1,6 is placed, or the other members may be placed so as to be in contact with the portion. The other members used in combination with the sound insulation structure 1,6 may be made of various materials.

[0049] Examples of locations in an automobile where the sound insulation structures 1, 6 of the present invention are installed include, in the engine compartment, engine head covers, engine body covers, hood insulators, front-dash insulators, air box walls, air intake cleaners, dust side ducts, under covers, etc.; in the cabin, examples include dash insulators, dash panels, floor carpets (floor silencers), spacers, door trims, the inside of door trims, instrument panels, instrument center boxes, instrument upper boxes, air conditioner housings, roof trims, the inside of roof trims, sun visors, air conditioning ducts for rear seats, cooling ducts of battery cooling systems in battery-equipped vehicles, cooling fans, center console trims, the inside of the console, parcel trims, parcel panels, seat headrests, front seat backs, rear seat backs, etc.; and in the trunk, examples include trunk side trims, the inside of trims, and drafter covers. In addition, the sound-insulating structures 1, 6 of the present invention can be installed within the frame of an automobile or between panels, and can also be installed in under-covers under the floor located outside the vehicle, fender protectors, back doors, wheel covers, aerodynamic covers for suspensions, and the like.

[0050] Specific examples and comparative examples of the sound insulation structure of the present invention will be described below. [Example 1] A sound-insulating structure 1 of Example 1 of the present invention has the same structure as that of the first embodiment shown in Figures 1A to 2B. The film portion 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 film part 2 of this embodiment is made of EPDM (ethylene-propylene-diene rubber) having a dynamic storage modulus (E') of 20.4 MPa and a loss tangent (tan δ) of 0.12 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 23.0 MPa and a loss tangent (tan δ) of 0.13 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 25.4 MPa and a loss tangent (tan δ) of 0.16 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 28.8 MPa and a loss tangent (tan δ) of 0.14 at 23°C and a frequency of 1000 Hz, a durometer A hardness of 70 according to JIS K6253, and a film thickness of 0.5 mm. The planar shape of this film part 2 has an area of ​​1000 cm. 2 If the square is square, the bending stiffness K is 67.2N / mm 2 The planar shape has an area of ​​400 cm 2 If the square shape is square, the bending stiffness K is 42.5N / mm 2 If the material of the film 2 is the same as that of the film 2, the film thickness is 3 mm, and the planar area is 1000 cm 2 When a square membrane is formed, its bending stiffness K is about 1.5×10 4 N / mm 2 It is.

[0051] The support wall portion 3 of this embodiment is made 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 (tan δ) 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 3 of this embodiment is made of EPDM having a dynamic storage modulus (E') of 13.2 MPa and a loss tangent (tan δ) of 0.12 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 15.0 MPa and a loss tangent (tan δ) of 0.14 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 17.4 MPa and a loss tangent (tan δ) of 0.17 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 20.2 MPa and a loss tangent (tan δ) of 0.16 at 23°C and a frequency of 1000 Hz, a durometer A hardness of 65 according to JIS K6253, a plate thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the film part 2. However, only the support wall 3 located on the outermost side has a plate thickness of half that, 0.8 mm. The compartments 5 defined by the multiple support walls 3 (first wall 3a and second wall 3b) are square, measuring 25 mm x 25 mm, and there are 49 compartments 5 in the 200 mm x 200 mm square area (evaluation surface) of the membrane 2. However, the drawing shows only a portion of this area. The weight 4 is cylindrical, with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane 2) of 6 mm.

[0052] Of the weight portion 4, the spring portion 4a, which is the portion attached to the membrane portion 2, is 3 mm in height and is made 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 (tan δ) 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 in this embodiment has a dynamic storage modulus (E') of 0.60 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 1 Hz, a dynamic storage modulus (E') of 0.74 MPa and a loss tangent (tan δ) of 0.24 at 23° C. and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.97 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 100 Hz, and a dynamic storage modulus (E') of 1.31 MPa and a loss tangent (tan δ) of 0.16 at 23° C. and a frequency of 1000 Hz, and is made of silicone rubber with a durometer A hardness of 10 according to JIS K6253. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side attached to the membrane portion 2, also has a height of 3 mm and is made of stainless steel (SUS304) having rigidity. The mass of the weight 4 is approximately 0.8 g, and has a resonance that shows a peak frequency at 600 Hz to 650 Hz in the direction perpendicular to the installation surface of the weight 4. The height of the entire sound insulation structure 1 is 10.5 mm, and the overall surface density of one section 5 including the film portion 2, the support wall portion 3, and the weight 4 is 2.97 kg / m 2 It is.

[0053] As shown in FIG. 13, the end face of the support wall 3 of the sound insulation structure 1 opposite to the side attached to the film 2 was placed on a 0.8 mm thick iron plate 8, and the sound insulation was measured with the surface of the iron plate 8 opposite to the side on which the sound insulation structure 1 was placed as the incident sound side. Specifically, in accordance with the intensity method shown in JIS A1441-1, a test equipment room with a reverberation room as the sound source room and a semi-anechoic room as the sound receiving room was used, and the sound transmission loss (transmission loss) [dB] was obtained for the 1 / 3 octave band center frequency [Hz] by 1 / 3 octave band analysis. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss was obtained and is shown in FIG. 14A to 14F and 14K. The larger the sound transmission loss, the higher the sound insulation. In the 1 / 3 octave band center frequency [Hz] shown in FIG. 14A to 14K, 1 kHz is 1000 Hz, and the prefix "k" means 1000.

[0054] [Comparative Example 1] As Comparative Example 1, as shown in Fig. 15, sound insulation was measured with nothing placed on a 0.8 mm thick iron plate 8, and the relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Fig. 14A. This shows the state where no sound insulation structure is provided. The surface density of this structure is 6.02 kg / m 2 It is.

[0055] [Comparative Example 2] As Comparative Example 2, a member having the same mass as the sound insulation structure 1 of Example 1 is placed on a 0.8 mm thick iron plate 8. The theoretical sound insulation value calculated based on the mass law was obtained, and the relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Figure 14A. The surface density of this structure is 8.99 kg / m 2 It is.

[0056] [Comparative Example 3] As Comparative Example 3, as shown in Figs. 16A and 16B, a sound insulation structure consisting of only a film portion 2 and a supporting wall portion 3 was placed on a 0.8 mm thick iron plate 8, and the sound insulation was measured. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Figs. 14A to 14B. The film portion 2 and supporting wall portion 3 of this example are the same as those of Example 1, but there is no weight portion 4. The surface density of this structure is 2.43 kg / m 2 It is.

[0057] [Example 2] A sound insulation structure 6 of Example 2 of the present invention has the same structure as that of the second embodiment shown in Figures 6A and 6B. The film portion 2 and the supporting wall portion 3 of this example are the same as those of Example 1. The weight portion 7 is made of EPDM having a durometer A hardness of 65 according to JIS K6253-3, and is cylindrical with a diameter of 13 mm and a height (dimension in the direction perpendicular to the film portion 2) of 5 mm. The mass of the weight portion 7 is about 0.85 g, and the surface density of this configuration is 3.04 kg / m 2 As shown in Fig. 17, the end face of the supporting wall portion 3 of the sound-insulating structure 6 opposite to the side attached to the film portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation was measured, and the result is shown in Fig. 14B.

[0058] [Example 3] A sound insulation structure 6 according to Example 3 of the present invention shown in Figures 18A and 18B has the same structure as Example 2, but has a weight portion 7 that is smaller than the weight portion 7 of Example 2. The film portion 2 and supporting wall portion 3 of this example are the same as the film portion 2 and supporting wall portion 3 of Example 1. The weight portion 7 is made of EPDM having a durometer A hardness of 65 according to JIS K6253-3, and is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the film portion 2) of 5 mm. The mass of the weight portion 7 is approximately 0.15 g. The surface density of this configuration is 2.54 kg / m 2 As shown in Fig. 18B, the end face of the supporting wall portion 3 of the sound-insulating structure 6 opposite to the side attached to the film portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation was measured, and the result is shown in Fig. 14B.

[0059] [Example 4] A sound insulation structure 1 (not shown) of Example 4 of the present invention has the same structure as Example 1, but has a supporting wall portion 3 that is softer than the supporting wall portion 3 of Example 1. The film portion 2 and weight portion 4 of this example are the same as the film portion 2 and weight portion 4 of Example 1. The supporting wall portion 3 of this example is made 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 at a frequency of 1 Hz to 1000 Hz, and a loss tangent (tan δ) of 0.01 or more and 0.50 or less at 23°C and at a frequency of 1 Hz to 1000 Hz. More specifically, the supporting wall 3 of this embodiment is made of EPDM having a dynamic storage modulus (E') of 1.48 MPa and a loss tangent (tan δ) of 0.07 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 1.72 MPa and a loss tangent (tan δ) of 0.12 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 2.00 MPa and a loss tangent (tan δ) of 0.11 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 2.33 MPa and a loss tangent (tan δ) of 0.12 at 23°C and a frequency of 1000 Hz, a durometer A hardness of 30 according to JIS K6253-3, a plate thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the film part 2. However, only the supporting wall 3 located on the outermost side has a plate thickness of half that, 0.8 mm. The areal density of this configuration is 2.52 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14C.

[0060] [Comparative Example 4] The sound insulation structure of Comparative Example 4 (not shown) has substantially the same structure as that of Example 1, but has a supporting wall portion 3 that is harder and less flexible than the supporting wall portion 3 of Example 1. The film portion 2 and the weight portion 4 of this comparative example are the same as the film portion 2 and the weight portion 4 of Example 1. The support wall 3 of this comparative example is made of polylactic acid (PLA resin) having a dynamic storage modulus (E') of 2.03 GPa and a loss tangent (tan δ) of 0.0045 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 2.04 GPa and a loss tangent (tan δ) of 0.000060 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 2.05 GPa and a loss tangent (tan δ) of 0.045 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 2.07 GPa and a loss tangent (tan δ) of 0.0079 at 23°C and a frequency of 1000 Hz, and its shape and dimensions are the same as those of the support wall 3 of Example 1. The surface density of this configuration is 2.63 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14C.

[0061] [Example 5] The sound insulation structure 1 (not shown) of Example 5 has the same structure as Example 1, but has a film portion 2 that is softer than the film portion 2 of Example 1. The supporting wall portion 3 and weight portion 4 of this example are the same as the supporting wall portion 3 and weight portion 4 of Example 1. The film portion 2 of this example is made of EPDM having a durometer A hardness of 30 according to JIS K6253-3, which is the same material as the supporting wall portion 3 of Example 4, and its shape and dimensions are the same as the film portion 2 of Example 1. The surface density of this configuration is 2.83 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14D.

[0062] [Example 6] The sound insulation structure 1 of Example 6 shown in Figures 19A and 19B has the same structure as Example 1, but has a section 5 that is wider than the section 5 of Example 1. The film section 2 and weight section 4 of this example are the same as the film section 2 and weight section 4 of Example 1. The support wall section 3 itself of this example is the same as the support wall section 3 of Example 1, but is arranged with a wider interval between them than in Example 1. As a result, each section of this example is a square of 50 mm x 50 mm, and its area is 2500 mm. 2 The areal density of this configuration is 1.60 kg / m 2 There are nine sections 5 in a 200 mm × 200 mm square area (evaluation surface) of the membrane 2. However, the drawing shows only a part of this area. As shown in Fig. 19B, the end face of the supporting wall 3 of the sound insulation structure opposite to the side attached to the membrane 2 was placed on a 0.8 mm thick iron plate 8 to determine the sound insulation, which is shown in Fig. 14E.

[0063] [Example 7] The sound insulation structure 1 (not shown) of Example 7 has the same structure as Example 1, but the weight portion 4 is cylindrical with a diameter of 13 mm and a height (dimension in the direction perpendicular to the film portion 2) of 9 mm. Of this weight portion 4, the spring portion 4a which is the portion attached to the film portion 2 has a height of 4 mm and is made 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 at frequencies of 1 Hz to 1000 Hz, and a loss tangent (tan δ) of 0.01 or more and 0.50 or less at 23°C and at frequencies of 1 Hz to 1000 Hz. More specifically, the spring portion 4a in this embodiment is made of polyurethane foam having a dynamic storage modulus (E') of 0.06 MPa and a loss tangent (tan δ) of 0.15 at 1 Hz at 23° C., a dynamic storage modulus (E') of 0.07 MPa and a loss tangent (tan δ) of 0.15 at 10 Hz at 23° C., a dynamic storage modulus (E') of 0.08 MPa and a loss tangent (tan δ) of 0.15 at 100 Hz at 23° C., and a dynamic storage modulus (E') of 0.10 MPa and a loss tangent (tan δ) of 0.15 at 1000 Hz at 23° C. The mass portion 4b, which is the part of the weight portion 4 opposite to the side attached to the film portion 2, has a height of 5 mm and is made of EPDM having a durometer A hardness of 65 according to JIS K6253-3. The mass of the weight portion 4 is about 1.0 g.

[0064] The membrane part 2 and the supporting wall part 3 of this embodiment are the same as the membrane part 2 and the supporting wall part 3 of the embodiment 1. The surface density of this structure is 3.08 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14F.

[0065] [Example 8] The sound insulation structure 1 (not shown) of Example 8 has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. The film portion 2 and the supporting wall portion 3 of this example are the same as the film portion 2 and the supporting wall portion 3 of Example 1, but the weight portion 4 of this example is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The spring portion 4a, which is the part of the weight portion 4 attached to the film portion 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the film portion 2) of 3 mm, and is made of the same material (silicone rubber with a durometer A hardness of 10 according to JIS K6253-3) as the spring portion 4a of the weight portion 4 of Example 1. The mass portion 4b, which is the part of the weight portion 4 opposite to the side attached to the film portion 2, is cylindrical with a diameter of 13 mm and a height of 5 mm, and is made of EPDM with a durometer A hardness of 65 according to JIS K6253-3. The mass of the weight 4 is approximately 1.0 g. The surface density of this structure is 3.13 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Figures 14F to 14G.

[0066] [Example 9] The sound insulation structure 1 (not shown) of Example 9 has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. The film portion 2 and weight portion 4 of this example are the same as the film portion 2 and weight portion 4 of Example 8, but the support wall portion 3 of this example is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a plate thickness of 1.6 mm, and a height of 10 mm in the direction perpendicular to the film portion 2. The surface density of this structure is 2.81 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Figures 14G to 14I.

[0067] [Example 10] The sound insulation structure 1 of Example 10 shown in Fig. 20 has the same structure as the modified example of the first embodiment shown in Figs. 3A and 3B. The film portion 2 and weight portion 4 of this example are the same as the film portion 2 and weight portion 4 of Example 9, but the support wall portion 3 of this example is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a plate thickness of 1.6 mm, and a height of 14 mm in the direction perpendicular to the film portion 2. The surface density of this structure is 3.16 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14H.

[0068] [Example 11] The sound insulation structure 1 of Example 11 shown in Figures 21A and 21B has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. Figure 21A is a perspective view of the sound insulation structure 1, and Figure 21B is a cross-sectional view taken along line BB. The film portion 2 and weight portion 4 of this example are the same as the film portion 2 and weight portion 4 of Example 9, but in this example, some support wall portions 3d among the multiple support wall portions are higher in height in a direction perpendicular to the film portion 2 than the other support wall portions 3c. That is, the sound insulation structure 1 of this example has support wall portions (some support wall portions) 3d that are high in height like the support wall portions 3 of Example 10, and support wall portions (other support wall portions) 3c that are low in height like the support wall portions 3 of Example 9. Specifically, the support wall 3c is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a plate thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the film portion 2, and the support wall 3d is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a plate thickness of 1.6 mm, and a height of 15 mm in a direction perpendicular to the film portion 2. The support wall 3d has a height 1.5 times that of the support wall 3c. In this embodiment, as shown in Figs. 21A and 21B, rows in which high support wall portions 3d are arranged and rows in which only low support wall portions 3c are arranged are alternately positioned. As a result, of the 49 square sections 5 arranged in a 7 x 7 grid, 16 sections 5 are sections surrounded by high support wall portions 3d. The surface density of this configuration is 3.02 kg / m 2The end face of the supporting wall portion 3d of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on an iron plate 8 having a thickness of 0.8 mm, and the sound insulation was measured, and the result is shown in FIG.

[0069] [Example 12] The sound insulation structure 1 (not shown) of Example 12 has the same structure as the modified example of the first embodiment shown in Figs. The membrane portion 2 and supporting wall portion 3 in this embodiment are formed by integral molding of a styrene-based thermoplastic elastomer (TPS) having 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, a dynamic storage modulus (E') of 9.19 MPa and a loss tangent (tan δ) of 0.11 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 10.3 MPa and a loss tangent (tan δ) of 0.08 at 23°C and a frequency of 1000 Hz, a durometer A hardness of 50 according to JIS K6253, a thickness of the membrane portion 2 of 1.0 mm, a plate thickness of the supporting wall portion 3 of 1.2 mm, and a height of 10 mm in the direction perpendicular to the membrane portion 2. The areal density of this configuration is 2.56 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14J.

[0070] [Example 13] The sound insulation structure 1 (not shown) of Example 13 has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. The film portion 2 and the supporting wall portion 3 of this example are the same as the film portion 2 and the supporting wall portion 3 of Example 12. The weight portion 4 of this example is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The spring portion 4a, which is the part of the weight portion 4 that is attached to the membrane portion 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane portion 2) of 3 mm, and is made of TPS with a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tan δ) 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 (tan δ) of 0.04 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.19 MPa and a loss tangent (tan δ) of 0.25 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 0.23 MPa and a loss tangent (tan δ) of 0.04 at 23°C and a frequency of 1000 Hz, and a durometer A hardness of 0 according to JIS K6253. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side attached to the membrane portion 2, is cylindrical with a diameter of 11 mm and a height of 6 mm, and is made of EPDM having a durometer A hardness of 70 according to JIS K6253-3. The surface density of this structure is 2.50 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14J.

[0071] [Example 14] The sound insulation structure 1 (not shown) of Example 13 has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. The film portion 2 and the supporting wall portion 3 of this example are the same as the film portion 2 and the supporting wall portion 3 of Example 12. The weight portion 4 of this example is composed of a small-diameter cylindrical spring portion 4a and a large-diameter cylindrical mass portion 4b. The spring portion 4a, which is the part of the weight portion 4 that is attached to the film portion 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the film portion 2) of 3 mm. The mass portion 4b, which is the part of the weight portion 4 opposite to the side that is attached to the film portion 2, is cylindrical with a diameter of 9 mm and a height of 6 mm. The spring portion 4a and the mass portion 4b of the weight portion 4 in this embodiment are made of TPS having a dynamic storage modulus (E') of 0.21 MPa and a loss tangent (tan δ) of 0.04 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 0.23 MPa and a loss tangent (tan δ) of 0.03 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.29 MPa and a loss tangent (tan δ) of 0.05 at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 0.25 MPa and a loss tangent (tan δ) of 0.17 at 23°C and a frequency of 1000 Hz, and a durometer A hardness of 5 according to JIS K6253. The areal density of this configuration is 2.50 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14J.

[0072] [Comparative Example 5] As Comparative Example 5, similar to Comparative Example 3, a sound insulation structure consisting of only a film portion 2 and a supporting wall portion 3 was placed on a 0.8 mm thick iron plate 8 as shown in Figs. 16A and 16B, and the sound insulation was measured. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Fig. 14J. The film portion 2 and supporting wall portion 3 of this example are different from the film portion 2 and supporting wall portion 3 of Example 1 and Comparative Example 3, but are the same as the film portion 2 and supporting wall portion 3 of Example 12. Furthermore, the sound insulation structure of this comparative example does not have a weight portion 4. The surface density of this configuration is 1.88 kg / m 2 It is.

[0073] [Comparative Example 6] The sound insulation structure 1 (not shown) of Comparative Example 6 has the same structure as that of Example 1, but has a film portion 2 made of a resin material with a thinner thickness than that of Example 1. The supporting wall portion 3 and the weight portion 4 of this example are the same as those of Example 1. The film portion 2 of this comparative example is made of low-density polyethylene (LDPE) with a thickness of 0.05 mm. The surface density of this structure is 2.25 kg / m 2 The end face of the supporting wall portion 3 of the sound-insulating structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in FIG. 14K.

[0074] [result] The results of comparing the above-mentioned Examples 1 to 14 of the present invention with Comparative Examples 1 to 6 will be described. Referring to 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, the sound insulation structure 1 of Example 1 provides a sound insulation effect significantly greater than the theoretical value based on the mass law (Comparative Example 2) in the frequency band higher than 630 Hz, demonstrating the great effect of the present invention. Furthermore, it can be seen that Example 1 having the weight portion 4 has a greater sound insulation property than Comparative Example 3, particularly in the frequency band lower than 1.25 kHz.

[0075] 14B, it can be seen that the sound insulation structure 1 (Example 1) of the first embodiment of the present invention and the sound insulation structure 6 (Examples 2 and 3) of the second embodiment of the present invention can provide a similarly good sound insulation effect. When the weight 4 itself constitutes a spring mass resonator as in Example 1, particularly good sound insulation is obtained near a frequency (for example, 630 Hz to 1000 Hz) where the vibration of the film part 2 is reduced by the resonance of the spring mass resonator. On the other hand, when the spring mass resonator is constituted by the weight 7 and the film part 2 as in Examples 2 and 3, the frequency band where sound insulation is particularly good can be adjusted by the weight of the weight 7. For example, when the weight 7 has a mass similar to that of the weight 4 of Example 1, the frequency band where sound insulation is particularly good is around 1000 Hz, and when the weight 7 is made lighter, the frequency band where sound insulation is particularly good can be shifted to the higher frequency side.

[0076] 14C, it can be seen that if the support wall 3 of the sound insulation structure is not made of a flexible material, the sound insulation is poor, but if the support wall 3 is made of a flexible material, a good sound insulation effect can be obtained. This is thought to be because if the support wall 3 is made of a hard material rather than a flexible material, vibrations are easily transmitted to the film 2 through the support wall 3, whereas if the support wall 3 is made of a flexible material, vibrations are less likely to be transmitted to the film 2 through the support wall 3. The frequency band in which sound insulation is particularly good can be adjusted by changing the hardness of the support wall 3. For example, if the support wall 3 is made softer, the frequency band in which sound insulation is particularly good can be shifted to the lower frequency side.

[0077] 14D, it can be seen that if the film part 2 of the sound insulation structure is too soft, the sound insulation performance is somewhat reduced. This is thought to be because if the film part 2 is too soft, vibrations of a degree sufficient for the spring mass resonator to function adequately are not transmitted to the spring mass resonator.

[0078] Referring to FIG. 14E, it can be seen that if each section 5 of the membrane section 2 defined by the support wall section 3 of the sound insulation structure is too large, the sound insulation performance is somewhat reduced. This is thought to be because if each section 5 is too large, the spring mass resonator does not function sufficiently, and the vibration reduction effect is reduced. Therefore, each section 5 is made relatively small (for example, 1000 mm 2 It is preferable that

[0079] 14F shows that even if the material and shape of the weight 4 of the sound-insulating structure 1 are different, as long as the material and shape are within the preferred range, the sound-insulating function of the present invention is exhibited. Therefore, it is clear that the material and shape of the weight 4, etc. can be freely set within the preferred range.

[0080] 14G, it can be seen that a similar sound insulation effect can be obtained even if the durometer A hardness of the supporting wall 3 according to JIS K6253-3 is somewhat different. And, referring to FIG. 14H, it can be seen that a good sound insulation effect can be obtained by a configuration in which the supporting wall 3 has a high height extending in a direction perpendicular to the film 2. This is because when the supporting wall 3 is high, the thickness of the air layer located between the mounting surface (iron plate 8 in each embodiment) on which the sound insulation structures 1, 6 are placed and the film 2 is large, so that the frequency band of the air resonance transmission changes, the effect of sound insulation inhibition in the target frequency band is reduced, and sound insulation in the low frequency range (for example, around 500 Hz) is particularly increased.

[0081] Referring to FIG. 14I, it can be seen that a good sound insulation effect can be obtained even if only some of the support walls 3d among the multiple support walls are made high in height in the direction perpendicular to the film part 2 and the other support walls 3c are made low in height. Even if only some of the support walls 3d are made high in height, the thickness of the air layer located between the mounting surface (iron plate 8 in each embodiment) on which the sound insulation structure 1, 6 is placed and the film part 2 becomes large, as in the case of a configuration in which all of the support walls 3d are made high, and as described above, the sound insulation becomes large, especially in the low frequency range (for example, around 500 Hz). By making only some of the support walls 3d high, the thickness of the air layer is increased while suppressing an increase in the weight of the entire sound insulation structure 1, 6, and the sound insulation structure 1, 6 can be easily stably mounted on mounting surfaces of various shapes, including curved surfaces. In other words, a lightweight sound insulation structure 1, 6 with good sound insulation properties in the low frequency range can be provided. However, if there are too few support walls 3d with high heights, the sound insulation structure 1, 6 cannot be stably mounted. support If the number of support walls 3c and 3d is too large, the weight of the entire sound insulation structure 1 and 6 increases. Therefore, it is preferable that the section 5 surrounded by the high support wall portion 3d is 5% or more of the total section 5 of the sound insulation structure 1 and 6. Membrane part When viewed in a cross section parallel to 2, it is preferable that the total cross-sectional area of ​​the taller support wall portion 3d is 10% or more of the total cross-sectional area of ​​all the support walls 3c, 3d of the sound insulation structure 1, 6. In Example 11, a 20 mm×20 mm (area 400 cm) portion of the membrane portion 2, which has a planar shape of 25 mm×25 mm square, is2 ) there are 7 × 7 = 49 compartments 5 as shown in FIG. 21A, of which 16 compartments 5 are compartments 5 surrounded by high support wall portions 3d, which is a preferable proportion of 32.6%.

[0082] Incidentally, even when the height of all of the support wall portions 3 is high as in Example 10, or when the height of only some of the support wall portions 3d is high as in Example 11, it is preferable to keep the overall height of the sound-insulating structures 1, 6 to 20 mm or less, as described above, in order to suppress an increase in the overall weight of the sound-insulating structures 1, 6 and restrictions on installation.

[0083] Referring to FIG. 14J, it can be seen that even if the film portion 2 and the supporting wall portion 3 are formed by integral molding of a thermoplastic material, good sound insulation can be obtained by providing the weight portion 4. As in Example 13, in a spring mass resonator consisting of the spring portion 4a and the mass portion (mass portion) 4b of the weight portion 4, if the spring portion 4a is softer, the resonance frequency shifts to the low frequency side, and a large sound insulation effect can be obtained on the low frequency side. In this way, by changing the configuration of the weight portion 4, it is possible to adjust the sound insulation frequency band. Also, as in Example 14, it can be seen that good sound insulation can be obtained even if the weight portion 4 is configured to be made of a single material. Therefore, productivity can be improved by manufacturing the weight portion from a single material.

[0084] 14K, if the film 2 is made of a thin resin material (film), the sound insulation performance is reduced, so it is preferable that the film 2 has a certain thickness. Compared to the elastomer material such as EPDM in Example 1, the resin material such as LDPE in Comparative Example 6 is hard, so it is possible to make the film thin, but if the film thickness is not greater than a certain level, it is too soft for the film 2 to transmit vibrations to the weight 4 to the extent that the spring mass resonator consisting of the spring portion 4a and the mass portion 4b of the weight 4 can function sufficiently. Therefore, it is preferable that the film 2 has a certain thickness.

[0085] [Soundproofing structure] A soundproof structure 11 including the soundproof structures 1 and 6 of the present invention described above, which has improved soundproofing properties and is easy to install, will be described. First, a side view of an automobile, which is an example of a vehicle equipped with the soundproof structure 11, is shown in FIG. 22. The soundproof structure 11 of the present invention is arranged so as to overlap a panel (dash panel) 14 provided at the boundary between an engine room 12 and a passenger compartment 13 of the automobile. A side view of the soundproof structure 11 is shown in FIG. 23, a perspective view from the front side is shown in FIG. 24, and a cross-sectional view of line CC in FIG. 24 is shown in FIG. 25. The soundproof structure 11 is composed of a soundproof plate-shaped part 10 and a soundproof structure part 9 positioned side by side in a plane. The soundproof structure part 9 has the same configuration as any of the soundproof structures 1 and 6 of the present invention described above. That is, the soundproof structure part 9 is composed of any of the soundproof structures 1 and 6 of the present invention described above. In this example, a large-area soundproof plate-shaped portion 10 and two soundproof structural portions 9 are formed integrally or joined together to form a soundproof structure 11 that can be handled as a single component.

[0086] The soundproof plate-like part 10 has a single-layer structure consisting of either a layer of a sound-absorbing material such as felt, polyurethane foam, or glass wool, or a layer of a sound-insulating material such as a resin film or a rubber sheet, or a laminated structure of these. The soundproof plate-like part 10 is a plate-like member shaped to fit the panel 14, and may have different thicknesses depending on the part. As an example, the soundproof plate-like part 10 has a thickness ranging from a thin part less than 5 mm to a thick part about 40 mm. The soundproof plate-like part 10 may have a substantially similar structure or a similar structure to the dash silencer described in Patent Documents 1 and 2.

[0087] An example of the sound insulation structure 9 has the same configuration as the sound insulation structure 1 shown in Figs. 1A to 2B, that is, the sound insulation structure 9 is made of the sound insulation structure 1 of the present invention described above. This sound insulation structure 9 has an elastic sheet-like film 2, an elastic support wall 3 standing substantially vertically from the film 2, and an elastic weight 4 standing substantially vertically from the film 2. Each of the weights 4 located in each section 5 constitutes a spring mass resonator having an elastic spring 4a and a mass (mass) 4b having a larger mass than the spring 4a. Since this sound insulation structure 9 has the same configuration as the sound insulation structure 1 shown in Figs. 1A to 2B, as described above, the vibration of the film 2 is controlled by the action of the spring mass resonator constituted by the spring 4a and the mass 4b of the weight 4. In particular, in a specific frequency range (for example, a frequency of 1000 Hz or less), the membrane vibration is significantly reduced, and high sound insulation is exhibited.

[0088] In this soundproofing structure 11, the soundproofing structure 9 having the above-mentioned configuration is arranged in a portion of the vehicle where sound propagation is particularly strong. In the example shown in FIG. 22, the soundproofing structure 11 is arranged so as to overlap the panel 14 located at the boundary between the engine room 12 and the passenger compartment 13 of the automobile. The soundproofing structure 9 is arranged at two locations facing the front tire, which is a portion where road noise propagation is particularly strong. If the entire soundproofing structure 11 arranged so as to overlap the panel 14 were composed of the soundproofing structure 9 having the above-mentioned configuration, the soundproofing effect would be high, but the weight of the soundproofing structure 11 would be large, which may adversely affect the performance of the vehicle. In contrast, in the soundproofing structure 11 of this embodiment, the soundproofing structure 9 having a particularly high soundproofing effect is arranged in a portion where sound propagation is strong (for example, a position facing the tire), and the soundproofing plate-shaped portion 10 having a simple structure is arranged in a portion where sound propagation is not so strong (a position other than the position facing the tire). This makes it possible to efficiently prevent sound from entering while minimizing the increase in weight. Not only the soundproof plate-like portion 10 formed to match the shape of the panel 14, but also the soundproof structure portion 9 can be easily and stably installed on mounting surfaces of various shapes without fixing them by adhesive or the like. Therefore, the soundproof structure 11 of this embodiment can be stacked on the panel 14 of a complex shape and held stably.

[0089] In this example, on one main surface of the soundproofing structure 11 (the surface facing the vehicle interior 13, facing the right side in Figs. 22 and 23, and the wide surface mainly shown in Fig. 24), the area occupied by the soundproofing structure 9 is preferably 5% to 95% of the entire area of ​​the soundproofing structure 11, more preferably 10% to 40% and even more preferably 20% to 30%. If the proportion of the area occupied by the soundproofing structure 9 is too small, the sound insulation of the soundproofing structure 11 equivalent to a dash silencer becomes insufficient. Also, if the proportion of the area occupied by the soundproofing structure 9 is too large, there is a drawback in that the sound pressure increases when the noise propagated to the vehicle interior side through the soundproofing structure 11 is reflected by the instrument panel and hits the surface of the soundproofing structure 11 on which the sound-absorbing material is not laminated and is reflected again, resulting in a muffled sound. In the example shown in Figs. 22 to 25, the area occupied by the soundproofing structure 9 is about 30% of the entire area of ​​the soundproofing structure 11.

[0090] In this example, the soundproof plate-like portion 10 and the sound insulating structure portion 9 are integrated. Specifically, a layer of soundproof material (felt, urethane, glass wool, etc.) or a layer of sound insulating material (resin film, rubber sheet, etc.) constituting the soundproof plate-like portion 10 and at least one of the film portion 2 and the supporting wall portion 3 of the sound insulating structure portion 9 are integrally molded by insert molding or the like, or are joined to each other by ultrasonic welding, adhesion with a hot melt adhesive, or fixing with clips, bolts, or rivets. This makes it easy to handle the soundproof structure 11 consisting of the soundproof plate-like portion 10 and the sound insulating structure portion 9.

[0091] The soundproof structure 11 of the present invention is very thin and lightweight, not only in the soundproof plate-like portion 10 but also in the soundproof structure portion 9 as described above, and can be easily placed on a curved or uneven surface, so that it is suitable for use by being placed on a panel of a vehicle, particularly an automobile (for example, panel 14 shown in Figs. 1A-1B). Examples of panels on which the soundproof structure 11 is placed may be the same as the panels on which the soundproof structures 1 and 6 described above are placed. The arrangement method, position and usage form of the soundproof structure 11 may be the same as the arrangement method, position and usage form of the soundproof structures 1 and 6 described above.

[0092] The soundproof structure 11 of the present invention has a soundproof structure part 9 having the same configuration as the soundproof structures 1 and 6 illustrated in the above-mentioned Examples 1 to 14, and additionally includes a soundproof plate-shaped part 10. Therefore, it can be said that the difference in soundproofing properties between the soundproof structures 1 and 6 of Examples 1 to 14 represents the difference in soundproofing properties between the soundproof structures 11. In addition, as described above, the soundproof structures 1 and 6 of Examples 1 to 14 have greater soundproofing properties than the structures of Comparative Examples 1 to 6, and it is considered that the soundproof structure 11 of the present invention exhibits even better soundproofing properties by virtue of the inclusion of the soundproof plate-shaped part 10.

[0093] The present invention includes the following configurations and methods. [1] A device comprising: a membrane portion having elasticity; a support wall portion having elasticity and standing on the membrane portion; and a weight portion standing on the membrane portion; the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; A sound-proof structure, characterized in that each of the weight portions constitutes a spring-mass resonator having a spring portion having elasticity and a mass portion having a mass greater than that of the spring portion. [2] The sound-proofing structure described in [1], wherein the membrane portion, the support wall portion and the spring portion are all made of either a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity. [3] The sound-proofing structure according to [1] or [2], wherein the membrane portion, the supporting wall portion and the spring portion all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and at a frequency of 1 Hz to 1000 Hz. [4] The sound-proofing structure according to any one of [1] to [3], wherein the film portion, the supporting wall portion and the spring portion 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. [5] A sound-proofing structure described in any of [1] to [4], wherein the spring portion of the weight portion is located on the side of the weight portion that is attached to the membrane portion, and the mass portion is located on the side opposite the side of the weight portion that is attached to the membrane portion. [6] The sound-proofing structure according to any one of [1] to [5], wherein the mass portion of the weight portion has a larger volume than the spring portion. [7] A sound-proofing structure according to any one of [1] to [6], wherein the mass portion of the weight portion is made of a material having a higher density than the spring portion. [8] A membrane portion having elasticity, a support wall portion standing on the membrane portion having elasticity, and a weight portion standing on the membrane portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; A sound-proofing structure, characterized in that the film portion serves as a spring portion and the weight portion serves as a mass portion to constitute a spring-mass resonator. [9] The sound-proofing structure described in [8], wherein the membrane portion and the supporting wall portion are both made of a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity.

[10] The sound-proofing structure according to [8] or [9], wherein the membrane portion and the supporting wall portion each have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and at a frequency of 1 Hz to 1000 Hz.

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

[10] , wherein the film portion and the supporting wall portion each have a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency range of 1 Hz to 1000 Hz.

[12] A sound-proofing structure described in any of [1] to

[11] , wherein the support wall portion includes a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending 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 extending in a second direction perpendicular to the first direction.

[13] A sound-proofing structure described in any of [1] to

[11] , wherein the support wall portion is cylindrical having a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or rectangular tubular having a polygonal cross-sectional shape that defines each of the compartments.

[14] The area of ​​each of said compartments is 100 mm 2 More than 1000mm 2 The sound insulation structure according to any one of [1] to

[13] below.

[15] The area of ​​the membrane is 1000 cm 2 The sound insulation structure according to any one of [1] to

[14] , wherein 10 to 1,000 of the compartments are provided per unit area.

[16] The area of ​​the membrane is 1000 cm 2

[15] The sound insulation structure according to

[15] , wherein 50 to 500 of the compartments are provided per unit area.

[17] A sound-proofing structure according to any one of [1] to

[16] , wherein the plate thickness of the support wall portion is 0.5 mm or more and 5.0 mm or less.

[18] The sound-proofing structure described in

[17] , wherein the plate thickness of the support wall portion is 1.0 mm or more and 3.0 mm or less.

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

[18] , wherein the film thickness of the film portion is 0.1 mm or more and 3.0 mm or less.

[20] A sound-proofing structure according to any one of [1] to

[19] , wherein the height in a direction perpendicular to the membrane portion is 5 mm or more and 20 mm or less.

[21] A sound-proofing structure according to any one of [1] to

[20] , wherein the height of the support wall portion extending in a direction perpendicular to the membrane portion is 5 mm or more and 20 mm or less.

[22] The sound-proofing structure according to

[21] , wherein the height of the support wall portion extending in a direction perpendicular to the membrane portion is 10 mm or more and 20 mm or less.

[23] A sound-proofing structure as described in any one of [1] to

[22] , having a plurality of the support wall portions, some of the support wall portions having a height extending in a direction perpendicular to the membrane portion greater than the other support wall portions.

[24] The sound-proofing structure described in

[23] , wherein the height of the support wall portion that is taller extending in a direction perpendicular to the membrane portion is greater than 10 mm and not greater than 20 mm, and the height of the other support wall portions is not greater than 10 mm.

[25] A sound-proofing structure according to any one of [1] to

[24] , wherein the height of the weight portion extending in a direction perpendicular to the membrane portion is 1 mm or more.

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

[25] , wherein the film 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 portion and a soundproof structure portion, The soundproof plate-shaped portion is a plate-shaped member made of a sound-absorbing material or a sound-insulating material, The sound insulation structure part is a sound insulation structure according to any one of [1] to

[26] , The membrane portion and the support wall part and the soundproofing plate-shaped portion are integrally formed or joined to each other, and the soundproofing plate-shaped portion and the soundproofing structure portion are positioned side by side in a plane.

[28] The soundproof structure described in

[27] , wherein the area of ​​the main surface of the soundproof structure occupied by the soundproof structure portion is 5% or more and 95% or less of the area of ​​the entire soundproof structure.

[29] The membrane portion and the support wall part The soundproof structure according to

[27] or

[28] , wherein at least one of the above and the soundproof plate-shaped portion is integrally formed by insert molding, or is joined to each other by ultrasonic welding, adhesion with a hot melt adhesive, or fastening with clips, bolts or rivets.

[30] A soundproofing structure described in any of

[27] to

[29] , wherein the soundproofing plate-shaped portion has a single-layer structure consisting of either a layer made of felt, urethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are laminated.

[31] A soundproof structure described in any of

[27] to

[30] , attached to an interior panel of a motor vehicle.

[32] A soundproof structure as described in

[31] , which is attached to a dash panel of an automobile, and each of the soundproof structural parts is provided in a position facing the tire. [Explanation of symbols]

[0094] 1,6 Sound insulation structure 2 Membrane part 3 Support wall section 3a 1st wall 3b 2nd wall part 3c Low supporting wall (other supporting wall) 3d Tall supporting wall (part of supporting wall) 4,7 Weight 4a Spring part 4b Mass part 5 Plots 8. Iron Plate 9 Soundproofing structure 10 Soundproof plate 11 Soundproofing structure 12 Engine Room 13 Cabin 14 Panel (Dash Panel)

Claims

1. The elastic support wall portion is provided on the membrane portion and has an elasticity, and a weight portion is provided on the membrane portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; A sound-proof structure, characterized in that each of the weight portions constitutes a spring-mass resonator having a spring portion having elasticity and a mass portion having a mass greater than that of the spring portion.

2. 2. The sound-proofing structure according to claim 1, wherein the membrane portion, the support wall portion and the spring portion are all made of a material having rubber elasticity but not energy elasticity, a material having energy elasticity but not rubber elasticity, or a material having both rubber elasticity and energy elasticity.

3. 3. The sound insulation structure according to claim 1, wherein the film portion, the support wall portion and the spring portion all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23° C. and at a frequency of 1 Hz to 1000 Hz.

4. 4. The sound insulation structure according to claim 3, wherein the film portion, the support wall portion and the spring portion all have a loss tangent of 0.01 or more and 0.50 or less at 23° C. and a frequency range of 1 Hz to 1000 Hz.

5. 3. The sound insulation structure according to claim 1, wherein the spring portion of the weight portion is located on the side of the weight portion that is attached to the membrane portion, and the mass portion is located on the side opposite the side of the weight portion that is attached to the membrane portion.

6. The sound insulation structure according to claim 5 , wherein the mass portion of the weight portion is larger in volume than the spring portion.

7. The sound-proof structure according to claim 1 , wherein the mass portion of the weight portion is made of a material having a higher density than the spring portion.

8. 2. The sound-proofing structure of claim 1, wherein the support wall portion includes a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending 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 extending in a second direction perpendicular to the first direction.

9. 2. The sound insulation structure according to claim 1, wherein the support wall portion is in the form of a cylinder having a circular, elliptical or oval cross-section that defines each of the compartments, or in the form of a square tube having a polygonal cross-section that defines each of the compartments.

10. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 2. The sound insulation structure according to claim 1, wherein:

11. The area of ​​the membrane is 1000 cm 2 The sound insulation structure according to claim 1 , wherein 10 to 1,000 of the compartments are provided per unit area.

12. The area of ​​the membrane is 1000 cm 2 The sound insulating structure according to claim 11, wherein the number of the compartments is between 50 and 500 per one unit.

13. 2. The sound insulation structure according to claim 1, wherein the plate thickness of the support wall portion is 0.5 mm or more and 5.0 mm or less.

14. The sound insulation structure according to claim 13, wherein the plate thickness of the support wall portion is 1.0 mm or more and 3.0 mm or less.

15. 2. The sound insulation structure according to claim 1, wherein the film thickness of the film portion is 0.1 mm or more and 3.0 mm or less.

16. 2. The sound insulation structure according to claim 1, wherein the height in a direction perpendicular to the film portion is 5 mm or more and 20 mm or less.

17. 2. The sound insulation structure according to claim 1, wherein the height of the support wall portion extending in a direction perpendicular to the film portion is 5 mm or more and 20 mm or less.

18. 18. The sound insulation structure according to claim 17, wherein the height of the support wall portion extending in a direction perpendicular to the film portion is 10 mm or more and 20 mm or less.

19. 2. The sound insulation structure according to claim 1, comprising a plurality of the support walls, some of the support walls being taller in height in a direction perpendicular to the film than the other support walls.

20. 20. The sound insulation structure according to claim 19, wherein the height of the support wall portion that is taller in the direction perpendicular to the membrane portion is greater than 10 mm and is not greater than 20 mm, and the height of the other support wall portions is not greater than 10 mm.

21. 2. The sound insulation structure according to claim 1, wherein the height of the weight portion extending in a direction perpendicular to the film portion is 1 mm or more.

22. 2. The sound insulation structure according to claim 1, wherein the film 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.

23. A soundproof structure comprising a soundproof plate portion and a soundproof structure portion, The soundproof plate-shaped portion is a plate-shaped member made of a sound-absorbing material or a sound-insulating material, The sound insulation structure part is made of the sound insulation structure according to claim 1, A soundproof structure, characterized in that at least one of the membrane portion and the support wall portion and the soundproof plate-shaped portion are formed integrally with or joined to each other, and the soundproof plate-shaped portion and the soundproof structure portion are positioned side by side in a plane.

24. 24. The soundproof structure according to claim 23, wherein an area of ​​the main surface of the soundproof structure occupied by the soundproof structure portion is 5% to 95% of an area of ​​the entire soundproof structure.

25. 24. The soundproof structure according to claim 23, wherein at least one of the membrane portion and the support wall portion and the soundproof plate portion are integrally formed by insert molding, or are joined to each other by ultrasonic welding, adhesion with a hot melt adhesive, or fixing with clips, bolts or rivets.

26. 24. The soundproof structure according to claim 23, wherein the soundproof plate-shaped portion has a single-layer structure consisting of either a layer made of felt, urethane or glass wool and a layer made of a resin film or a rubber sheet, or a multi-layer structure in which these are laminated.

27. 24. The acoustic structure of claim 23 attached to an interior panel of an automobile.

28. 28. The soundproof structure according to claim 27, which is attached to a dash panel of an automobile, and each of said soundproof structures is provided at a position facing a tire.

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