Sound insulation structure and soundproof structure

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

Sound-insulating and sound-proof structures

[0001] The present invention relates to a sound insulating structure and a soundproof structure.

[0002] In recent years, indoor spaces in buildings such as apartment buildings, office buildings, and hotels are required to provide quietness appropriate for the intended use of the room by blocking outdoor noise from outside the building, such as automobiles, trains, airplanes, ships, and the like, as well as equipment noise and human voices generated outside the room. Furthermore, in the interiors of vehicles such as automobiles, trains, airplanes, and ships, it is desirable to reduce noise by blocking wind noise and engine noise to provide a quiet and comfortable space for occupants. Therefore, there is a demand for means for blocking the transmission of noise and vibration from the outside to the inside of a building or vehicle, as well as for the transmission of noise and vibration from the outside to the inside of a building or vehicle, i.e., highly soundproofing components. In recent years, lightweight soundproofing components are required in buildings due to the increasing number of taller buildings, and lightweight soundproofing components are also required 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 automotive dash silencers (also called dash insulators). These dash silencers are laminated on a dash panel (dashboard) located at the boundary between the engine compartment and the passenger compartment, and suppress the intrusion of noise from the engine compartment 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 is an acoustic damping panel comprising a rigid frame divided into a plurality of individual cells, a sheet of flexible material, and a plurality of weights, each weight being fixed to the sheet of flexible material so 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 comprising an elastic sheet and a support portion that holds the sheet and divides the sheet into partitions, the relationship between the rigidity of the sheet in the partitions and the surface density of the sheet is specified.

[0006] The sound-proofing 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 that connects the weight portion to the substrate portion, and is configured so 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, blocking vibrations transmitted from the vehicle body through the frame.

[0008] Japanese Patent Application Laid-Open No. 2007-210381 Japanese Patent Application Laid-Open No. 2018-012353 Japanese Patent Application Laid-Open No. 2005-250474 International Publication No. WO2019 / 022245 Japanese Patent Application Laid-Open No. 2021-152584 Japanese Patent Application Laid-Open No. 2020-91481

[0009] The dash silencers described in Patent Documents 1 and 2 are unable to sufficiently reduce noise entering the vehicle cabin. In particular, road noise transmitted from the ground into the vehicle cabin is large, which may prevent the provision of a quiet and comfortable space for the occupants.

[0010] The acoustic damping panel described in Patent Document 3 has an inflexible, rigid frame, and vibrations are transmitted to the seat via this rigid frame, which may result in insufficient soundproofing. Furthermore, if the support surface on which the rigid frame is placed is curved or uneven, the acoustic damping panel may not be stably supported. In particular, since many panels of typical vehicles (e.g., automobiles) have curved or uneven surfaces, it is difficult to easily use the acoustic damping panel described in Patent Document 3 as a sound-insulating material for vehicles. Furthermore, the rigid frame has a large mass, and the increased mass of the sound-insulating material in the vehicle may be a problem.

[0011] The soundproofing material described in Patent Document 4 has a high support portion, i.e., a height extending from the seat in a direction perpendicular to the seat, preferably 25 mm or more. In order to stably support the seat with such a high support portion, the support portion preferably has rigidity. As a result, vibrations may be transmitted through the support portion, which may result in insufficient sound insulation. It may also be difficult to mount the soundproofing material on a curved or uneven surface, such as a vehicle (e.g., automobile) panel. Furthermore, such a high support portion increases the overall size and weight of the soundproofing material. When mounted on a vehicle panel, the soundproofing material may occupy a large amount of space inside the vehicle, reducing space efficiency, interfering with the installation of other components, or becoming a nuisance to occupants.

[0012] The sound-insulating material described in Patent Document 5 has a resonating section, which is the functional part that provides sound insulation, exposed and not covered by a support wall, etc., and if this resonating section comes into contact with other members or the human body, there is a risk that the sound-insulating properties will be reduced or changed. Therefore, a large space must be provided around the resonating section, which reduces space efficiency.

[0013] The vibration reduction device described in Patent Document 6 does not have a membrane portion, but consists of multiple vibrators and a frame connecting them. Therefore, like the sound-insulating material described in Patent Document 5, the vibrators, which are the functional components that provide the sound-insulating effect, are exposed, and if other components or the human body come into contact with these vibrators, the sound-insulating properties may be reduced or changed. Furthermore, the frame must be rigid to ensure a minimum structural strength for the vibration reduction device. As a result, vibrations are transmitted through the frame, which may result in insufficient sound insulation. Furthermore, it is difficult to mount the vibration reduction device described in Patent Document 6 on a curved or uneven surface, such as a vehicle panel.

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

[0015] A first sound-proofing structure of the present invention comprises an elastic membrane, an elastic support wall extending from the membrane, and a weight extending from the membrane, the membrane being divided into a plurality of compartments by the support wall, the weight being located in each of the compartments or in some of the compartments, each of the compartments having a weight located therein is provided with one weight, the height of the support wall extending in a direction perpendicular to the membrane is greater than the height of the weight extending in the direction perpendicular to the membrane, and each of the weights constitutes a spring-mass resonator having an elastic spring and a mass having a greater mass than the spring. Here, elasticity refers to the property of a solid material that is deformed by an external force and returns to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, "having elasticity" refers to having at least one of energy elasticity and rubber elasticity (entropy elasticity). The support wall portion and the spring portion may be made of 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. Similarly, the membrane portion may be made of 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. 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. Furthermore, the membrane portion, the support wall portion, and the spring portion may all be made of an elastic body whose loss tangent is 0.01 to 0.50 at 23°C and a frequency of 1 Hz to 1000 Hz.Specifically, the elasticity of the membrane portion, supporting wall portion, and spring portion is evaluated by measuring the frequency dependence 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') is 0.01 MPa or more and 100 MPa or less at 23°C and frequencies of 1 Hz to 1000 Hz. More preferably, the membrane portion and the supporting wall portion may each be made of an elastic body having a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23°C and frequencies of 1 Hz to 1000 Hz, and a loss tangent of 0.05 to 0.45 at 23°C and frequencies of 1 Hz to 1000 Hz. The spring portion of the weight portion may be located on the side of the weight portion attached to the membrane portion, and the mass portion may be located on the side of the weight portion opposite to the side 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.

[0016] A second sound-proofing structure of the present invention includes an elastic membrane, an elastic support wall extending from the membrane, and a weight extending from the membrane, the membrane being divided into a plurality of compartments by the support wall, the weight being located in each of the compartments or in some of the compartments, each of the weights being located in one of the compartments, the height of the support wall extending in a direction perpendicular to the membrane being greater than the height of the weights extending in the direction perpendicular to the membrane, the membrane serving as a spring and the weight serving as a mass, thereby forming a spring-mass resonator. The support wall may be 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. Similarly, the membrane portion may be made of 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. Both the membrane portion and the support wall portion may have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz. Furthermore, both the membrane portion and the support wall portion may be made of an elastic body having a loss tangent of 0.01 to 0.50 at 23°C and a frequency of 1 Hz to 1000 Hz. More preferably, both the membrane portion and the support wall portion may be made of an elastic body having 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 to 0.45 at 23°C and a frequency of 1 Hz to 1000 Hz.

[0017] The support wall may include a plurality of first walls extending in a direction perpendicular to the membrane and extending in a first direction parallel to the membrane, and a plurality of second walls extending in a direction perpendicular to the membrane and extending in a second direction perpendicular to the first direction. 2 More than 1000mm 2The area of ​​the membrane portion may be 1000 cm or less. 2 The number of compartments may be 10 to 1,000, and more preferably 50 to 500. The support wall portion may be cylindrical with a circular, elliptical, or oval cross-sectional shape defining each compartment, or may be rectangular with a polygonal cross-sectional shape defining each compartment, specifically a square, regular pentagon, or regular hexagonal cross-sectional shape. The thickness of the support wall portion may be 0.5 mm to 5.0 mm, and more preferably 1.0 mm to 3.0 mm. The film thickness of the membrane portion may be 0.1 mm to 3.0 mm. The height in a direction perpendicular to the membrane portion may be 5 mm to 20 mm. The height of the support wall portion extending in a direction perpendicular to the membrane portion may be 5 mm to 20 mm, and more preferably 10 mm to 20 mm. The support wall portion may have different heights in parts. The support wall may have a plurality of support walls, some of which may have a height extending in a direction perpendicular to the membrane portion greater than the other support walls. The height of the support walls that are taller in a direction perpendicular to the membrane portion may be greater than 10 mm and less than 20 mm, and the height of the other support walls (the shorter support walls) may be less than 10 mm. Note that the term "tall support walls" refers to support walls that are taller (e.g., by 1 mm or more) than the other support walls (the shorter support walls). The height of the weight portion extending in a direction perpendicular to the membrane portion may be 1 mm or more. The durometer A hardness of the membrane portion may be 30 or more, and the durometer A hardness of the support wall portion may be 1 or more and 90 or less. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3.

[0018] A first soundproof structure of the present invention is a soundproof structure comprising a soundproof plate portion and a soundproof structural portion, wherein the soundproof plate portion is a plate-shaped member made of a sound-absorbing or sound-insulating material, and the soundproof structural portion is the first soundproof structure described above, and at least one of the membrane portion and the support plate portion and the soundproof plate portion are integrally formed or joined to each other, and the soundproof plate portion and the soundproof structural 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 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. 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. Furthermore, the film 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 film portion, the support wall portion, and the spring portion is evaluated by measuring frequency dependence 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 a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less. Even more preferably, the film portion and the support wall portion may all have a dynamic storage modulus (E') at 23°C and 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 a frequency of 1 Hz to 1000 Hz of 0.05 or more and 0.45 or less. The spring portion may be located on the side of the weight portion attached to the membrane portion, and the mass portion may be located on the opposite side of the weight portion from the side 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 with a higher density than the spring portion.

[0019] A second soundproof structure of the present invention is a soundproof structure comprising a soundproof plate portion and a soundproof structural portion, wherein the soundproof plate portion is a plate-shaped member made of a sound-absorbing or sound-insulating material, and the soundproof structural portion is the second soundproof structure described above, and at least one of the film portion and the support plate portion is integrally formed with the soundproof plate portion or is joined to each other, and the soundproof plate portion and the soundproof structural portion are positioned side by side in a plane. The second soundproof structure may have the following configuration. Both the film portion and the support wall portion may be made of 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. Both the film portion and the support wall portion may have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz. Furthermore, the film portion and the supporting wall portion may both have a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23° C. More preferably, the film portion and the supporting wall portion may both have a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at a frequency of 1 Hz to 1000 Hz at 23° C., and a loss tangent of 0.05 or more and 0.45 or less at a frequency of 1 Hz to 1000 Hz at 23° C. On a main surface of the soundproof structure, the area occupied by the soundproof structure portion may be 5% or more and 95% or less of the area of ​​the entire soundproof structure.

[0020] The first soundproof structure and the second soundproof structure may have the following configuration: 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 with a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or may be rectangular with a polygonal cross-sectional shape that defines each of the compartments, specifically a square, regular pentagon or regular hexagonal cross-sectional shape. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2The area of ​​the membrane portion may be 1000 cm or less. 2 More preferably, the membrane portion has an area of ​​1000 cm or more and 1000 or less of the compartments. 2 There may be 50 to 500 compartments per unit area. The support wall portion may have a thickness of 0.5 mm to 5.0 mm. More preferably, the support wall portion may have a thickness of 1.0 mm to 3.0 mm. The film portion may have a film thickness of 0.1 mm to 3.0 mm. The height in a direction perpendicular to the film portion may be 5 mm to 20 mm. The support wall portion may have a height extending perpendicular to the film portion of 5 mm to 20 mm, and the height may vary in parts. The weight portion may have a height extending perpendicular to the film portion of 1 mm or more. 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 to 90. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3. At least one of the membrane and the support plate may be integrally formed with the soundproof plate by insert molding, or may be joined to each other by ultrasonic welding, adhesive bonding, adhesive tape, clips, bolts, staples, or rivets. The soundproof plate or the soundproof structure may be shaped to allow the soundproof structure and the soundproof plate to be joined together. For example, the soundproof plate may have a fitting hole formed therein, and the membrane may be joined by simply fitting a portion of the membrane into the fitting hole. The soundproof plate may have a single-layer structure consisting of either a layer of felt, urethane, or glass wool and a layer of a resin film or rubber sheet, or a multi-layer structure in which these layers are laminated. The soundproof plate may be attached to a panel inside the automobile. Furthermore, the soundproof plate may be attached to the automobile's dash panel, with a soundproof structure provided in a position facing the tire.

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

[0022] 1A is a perspective view of a sound-insulating structure according to a first embodiment of the present invention. FIG. 1A is a cross-sectional view taken along line A-A in FIG. 1A. FIG. 1B is an exploded perspective view of one section of the sound-insulating structure shown in FIGS. 1A and 1B. FIG. 1B is an exploded front view of one section of the sound-insulating structure shown in FIGS. 1A and 1B. FIG. 3A is a cross-sectional view of a sound-insulating structure according to another modification of the first embodiment of the present invention. FIG. 4A is a perspective view of a weight of the sound-insulating structure shown in FIG. 4A. FIG. 4A is a cross-sectional view of a sound-insulating structure according to yet another modification of the first embodiment of the present invention. FIG. 5A is a perspective view of a sound-insulating structure according to a second embodiment of the present invention. FIG. 6A is a cross-sectional view of a sound-insulating structure according to a modification of the second embodiment of the present invention. FIG. 7A is a perspective view of a weight of the sound-insulating structure shown in FIG. 7A. FIG. 7A is a plan view schematically showing one section of a sound-insulating structure according to another example of the sound-insulating structure according to the present invention. FIG. 7B is a plan view schematically showing one section of a sound-insulating structure according to another example of the sound-insulating structure according to the present invention. FIG. 7C is a plan view schematically showing multiple sections of a sound-insulating structure according to another example of the sound-insulating structure according to the present invention. FIG. 1 is a plan view schematically showing one section of yet another example of a sound-insulating structure of the present invention. FIG. 2 is a plan view schematically showing multiple sections of yet another example of a sound-insulating structure of the present invention. FIG. 3 is a plan view schematically showing one section of yet another example of a sound-insulating structure of the present invention. FIG. 4 is a plan view schematically showing multiple sections of yet another example of a sound-insulating structure of the present invention. FIG. 5 is a plan view schematically showing one section of yet another example of a sound-insulating structure of the present invention. FIG. 6 is a cross-sectional view showing the sound-insulating structure of Example 1 of the present invention attached to an iron plate. FIG. 7 is a graph showing the sound insulation properties of Example 1 of the present invention and Comparative Examples 1 to 3. FIG. 8 is a graph showing the sound insulation properties of Examples 1 and 4 of the present invention and Comparative Example 4. FIG. 9 is a graph showing the sound insulation properties of Examples 1 and 5 of the present invention. FIG. 10 is a graph showing the sound insulation properties of Examples 1 and 6 of the present invention. FIG. 11 is a graph showing the sound insulation properties of Examples 1, 7, and 8 of the present invention and Comparative Example 3. FIG. 12 is a graph showing the sound insulation properties of Examples 8 and 9 of the present invention. 10 is a graph showing the sound insulation properties of Examples 9 and 10 of the present invention. 11 is a graph showing the sound insulation properties of Examples 9 and 11 of the present invention.21A is a graph showing the sound insulation properties of Examples 12 to 14 of the present invention and Comparative Example 5. FIG. 22 is a graph showing the sound insulation properties of Example 1 of the present invention and Comparative Example 6. FIG. 23 is a cross-sectional view of the structure of Comparative Example 1. FIG. 24 is a perspective view of the sound insulation structure of Comparative Example 3. FIG. 25 is a cross-sectional view showing the sound insulation structure shown in FIG. 16A attached to an iron plate. FIG. 26 is a cross-sectional view showing the sound insulation structure of Example 2 of the present invention attached to an iron plate. FIG. 27 is a perspective view of the sound insulation structure of Example 3 of the present invention. FIG. 28 is a cross-sectional view showing the sound insulation structure of Example 6 of the present invention. FIG. 29 is a cross-sectional view showing the sound insulation structure shown in FIG. 30A attached to an iron plate. FIG. 31 is a cross-sectional view of the sound insulation structure of Example 10 of the present invention attached to an iron plate. FIG. 32 is a perspective view of the sound insulation structure of Example 11 of the present invention. FIG. 33 is a cross-sectional view showing the sound insulation structure of Example 11 of the present invention. FIG. 34 is a cross-sectional view showing the sound insulation structure of Example 21A attached to an iron plate. FIG. 35 is a side view of an automobile, which is an example of a vehicle equipped with a sound insulation structure of the present invention. FIG. 36 is a side view of the sound insulation structure shown in FIG. 37. FIG. 38 is a perspective view of the sound insulation structure shown in FIG. 38, viewed from the front side. FIG. 39 is a cross-sectional view along line C-C of FIG. 39.

[0023] Hereinafter, embodiments of the present invention will be described with reference to the drawings. [First Embodiment] Fig. 1A is a perspective view of a sound-insulating structure 1 according to a first embodiment of the present invention, and Fig. 1B is a cross-sectional view taken along line A-A in Fig. 1A and inverted. The sound-insulating structure 1 includes an elastic sheet-like film portion 2, an elastic support wall portion 3 extending substantially perpendicularly from the film portion 2, and a weight portion 4 extending substantially perpendicularly from the film portion 2. The film portion 2 is divided into a plurality of compartments (unit structures) 5 by the support wall portions 3. A weight portion 4 is located within each of the plurality of compartments 5, or within some of the plurality of compartments 5. In a compartment 5 having a weight portion 4 located therein, one weight portion 4 is located within each compartment 5. Fig. 2A is an exploded perspective view of one compartment 5 of the sound-insulating structure 1, and Fig. 2B is an exploded front view thereof. The height H1 of the support wall 3 extending from the membrane 2 in a direction perpendicular to the membrane 2 is greater than the height H2 of the weight 4 extending from the membrane 2 in a direction perpendicular to the membrane 2. Each weight 4 constitutes a spring-mass resonator having an elastic spring 4a and a mass 4b having a larger mass than the spring 4a. The term "elasticity" as used here refers to the property of a solid material that has been deformed by an external force and returns 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 presence of at least one of energy elasticity and rubber elasticity (entropy elasticity).

[0024] In this embodiment, the support wall 3 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, with the first walls 3a and the second walls 3b being integrated at their intersections. The plurality of first walls 3a and the plurality of second walls 3b thus form a lattice structure, and a plurality of compartments 5, each having a square planar shape and separated by the first walls 3a and the second walls 3b, are arranged in a matrix. In other words, the support wall 3 is a structure in which a plurality of rectangular tubes having a square cross-sectional shape are arranged side by side, defining each compartment 5. 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 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 portion of the weight portion 4 attached to the membrane portion 2 is the spring portion 4a, and the portion opposite the side attached to the membrane portion 2 is the mass portion 4b, which has a larger mass than the spring portion 4a. In the example shown in Figures 1A to 2B, the spring portion 4a and the mass portion 4b have the same shape and dimensions but are made of different materials. The spring portion 4a is made of a flexible material, and the mass portion 4b is made of a material with a higher density than the material constituting the spring portion 4a. A spring-mass resonator is constructed in which the spring portion 4a functions as a spring and the mass portion 4b functions as a mass. Note that in addition to the spring portion 4a of the weight portion 4, the membrane portion 2 may also function as part of the spring of the spring-mass resonator. Furthermore, the air in the space surrounded by the membrane portion 2 and the support wall portion 3 may function as part of the spring of the spring-mass resonator (an air spring). It is preferable that the spring portion 4 is also made of a flexible material, i.e., a material that has rubber elasticity but no energy elasticity, a material that has energy elasticity but no rubber elasticity, or a material that has both rubber elasticity and energy elasticity.

[0026] In the sound-insulating structure 1 of this embodiment, the vibration of the membrane 2 is controlled by the action of a spring-mass resonator formed by the spring portion 4a and mass portion 4b of the weight portion 4. In particular, membrane vibration is significantly reduced in a specific frequency range (for example, frequencies below 1000 Hz, which is the main frequency band of road noise in automobiles), resulting in a reduction in the sound radiated from the membrane 2 and a high level of sound insulation.

[0027] The section 5 of the sound-insulating structure 1 of this embodiment has a film portion 2 with an area of ​​1000 cm 2 Preferably, 10 to 1000 compartments are provided per compartment, and more preferably, 50 to 500 compartments are provided per compartment. If there are too few compartments 5, the effect of dividing the entire sound insulation structure 1 into a plurality of compartments 5 and having each compartment individually exhibit a 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 compartments 5, the weight of the entire sound insulation structure 1 may increase. The planar area of ​​each compartment 5 is 100 mm 2 More than 1000mm 2 It is preferable that the length is 200 mm or less. 2 Over 800mm 2 It is more preferable that the height be less than 5 mm. If the planar area of ​​each compartment 5 is too small, it may be difficult to arrange the weight 4 therein. On the other hand, if the area is too large, the effect of the weight 4 on the membrane 2 may be poor, resulting in poor sound insulation. The height of the entire sound-insulating structure 1 in a direction perpendicular to the membrane 2 is preferably 5 mm or more and 20 mm or less. If the height of the entire sound-insulating structure 1 is too low, the weight 4 may not be high enough to function as a spring-mass resonator. On the other hand, if the height is too high, the weight of the entire sound-insulating structure 1 may increase. Note that each drawing schematically illustrates each compartment 5 and support wall 3, etc., and the number and area of ​​compartments 5 and the height of the sound-insulating structure 1 may not be illustrated precisely or may not be consistent across the drawings. However, it is preferable that the number and area of ​​compartments 5 and the height of the sound-insulating structure 1 are appropriately designed to be within the aforementioned numerical ranges.

[0028] The film portion 2, supporting wall portion 3, and 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 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, preferably a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23° C. and a loss tangent (tan δ) of 0.05 or more and 0.50 or less at 23° C. The dynamic storage modulus (E') and 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 performance in the target frequency band may be deteriorated, and the shape retention of the film portion 2 and the support wall portion 3 may also be deteriorated. If the dynamic storage modulus (E') at 23°C and frequencies of 1 Hz to 1000 Hz is greater than 100 MPa, the vibration in the frequency band to be sound-insulated may be deteriorated, and the sound-insulating structure 1 may become rigid, which may also deteriorate the installability. The film portion 2 and the support wall portion 3 may be formed of the same material or different materials. It is preferable that the film portion 2 is also made of a flexible material, i.e., a material that has rubber elasticity but no energy elasticity, a material that has energy elasticity but no rubber elasticity, or a material that has both rubber elasticity and energy elasticity.

[0029] Since the weight portion 4 is attached to the film portion 2, it is preferable that the film portion 2 be a hard elastic film. The dynamic storage modulus (E') of the film portion 2 is preferably 15 MPa or more, and the thickness (film thickness) is preferably 0.1 mm to 3.0 mm, more preferably approximately 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 performance in the frequency band to be sound-insulated may deteriorate. If the thickness of the film portion 2 is greater 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 according to JIS K6253 of 30 or more, 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 performance in the frequency band to be sound-insulated may deteriorate. The rigidity (axial rigidity) k of the membrane part 2 is expressed as k = E' × A / L using the dynamic storage modulus E', the cross-sectional area A of the membrane part 2, and the thickness L of the membrane part 2. When the area of ​​the membrane part 2 to be evaluated for rigidity is 1000 cm 2 When the stiffness k is 10 6 N / mm or more 10 9 N / mm or less, and 6 N / mm or more 10 8 It is more preferable that the surface area of ​​the membrane portion 2 is 1000 cm or less. 2 When the stiffness is 10 6 If the film 2 has an area of ​​1000 cm, the film 2 may vibrate more slowly, resulting in a deterioration in sound insulation performance in the frequency band that is the target of sound insulation. 2 When the stiffness is 10 9 If it is greater than N / mm, the sound insulation structure 1 becomes too rigid and installation may become difficult. The bending rigidity K of the film 2 is expressed as K=E'×I from the dynamic storage 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 2 and the width b of the film 2. 3 When the area of ​​the membrane part 2 to be evaluated is 1000 cm 2 When this is the case, the bending stiffness K is 30 N / mm 2 10 above 5 N / mm 2 Preferably, it is 50 N / mm or less. 2 5x10 or more4 N / mm 2 It is more preferable that the area of ​​the membrane part 2 is 1000 cm or less. 2 The bending rigidity K is 30 N / mm 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 The bending rigidity K when 5 N / mm 2 If it is larger, the sound-insulating structure 1 becomes too rigid, which may result in poor 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 cross-linked (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. Examples of crosslinking (vulcanization) methods include a method of crosslinking (vulcanization) by heating using a crosslinking agent (vulcanizing agent) such as an organic peroxide, a phenolic resin, an oxime compound, sulfur, a sulfur-based compound, or a polyamine compound, or a method of crosslinking by irradiation with an electron beam. The crosslinked (vulcanized) rubber may contain various known compounding agents commonly used as rubber 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, mildew inhibitors, acid acceptors, silane coupling agents, antistatic agents, UV absorbers, etc.). These crosslinked (vulcanized) rubbers, crosslinking agents (vulcanizing agents), and compounding agents may be made from biomass materials.

[0031] Examples of thermoplastic elastomers include olefin-based thermoplastic elastomers, styrene-based thermoplastic elastomers, polyester-based thermoplastic elastomers, polyvinyl chloride-based thermoplastic elastomers, and ethylene-vinyl acetate-based thermoplastic elastomers. Examples of plastics 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, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, polyethylene, polypropylene, polyethylene terephthalate, thermoplastic polyurethane, or the like.

[0033] The support wall 3 is preferably made of a flexible material that is soft enough to support the membrane 2. The thickness of the support wall 3 is preferably 0.5 mm to 5.0 mm, and more preferably 1.0 mm to 3.0 mm. If the thickness of the support wall 3 is less than 0.5 mm, the shape retention of the sound-insulating structure 1 may be impaired. If the thickness of the support wall 3 is greater than 5.0 mm, the vibration of the membrane 2 may be impaired, which may result in poor sound insulation in the target frequency band and an increase in the weight of the entire sound-insulating structure 1. The height of the support wall 3 extending in a direction perpendicular to the membrane 2 is preferably 5 mm to 20 mm, and more preferably 10 mm to 20 mm. The support wall 3 may have partially different heights. If the height of the support wall 3 is partially different, the higher part may be 10 mm to 20 mm, more preferably 12 mm to 20 mm, and even more preferably 14 mm to 20 mm. If the height of the support wall portion 3 is too low, the weight portion 4 may not have a sufficient height as a spring-mass resonator. If the height of the support wall portion 3 is too high, the overall weight may increase. The material of the support wall portion 3 preferably has a durometer A hardness according to JIS K6253 of 1 or more and 90 or less, more preferably 10 or more and 70 or less. If the durometer A hardness of the support wall portion 3 is less than 1, the shape retention of the sound-insulating structure 1 may be deteriorated. If the durometer A hardness of the support wall portion 3 is greater than 90, vibrations from the support wall portion 3 may be transmitted to the membrane portion 2, deteriorating the sound-insulating performance and causing the sound-insulating structure 1 to become rigid, which may impair installation. The rigidity k of the support wall portion 3 is expressed as k = E' × A / L, where E' is the dynamic storage modulus of elasticity, A is the cross-sectional area of ​​the support wall portion 3, and L is the height of the support wall portion 3. When the area of ​​the support wall portion 3 to be evaluated for rigidity is 1000 cm, 2 When the stiffness k is 10 N / mm or more, 6 N / mm or less, and 2 N / mm or more 10 5 It is more preferable that the area of ​​the support wall 3 is 1000 cm or less. 2If the stiffness k is less than 10 N / mm when the area of ​​the support wall portion 3 is 1000 cm, 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, vibrations from the support wall portion 3 are transmitted to the membrane portion 2, which may deteriorate the sound insulation performance and may also make the sound insulation structure 1 too rigid, resulting in poor installation properties.

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

[0035] The material of the spring portion 4a of the weight portion 4 is a flexible material such as cross-linked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. The cross-linked (vulcanized) rubber, thermoplastic elastomer, and resin foam may be the same as the materials listed 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 may be 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 may not be able to sufficiently resonate in the frequency range to be sound-insulated, which may result in a deterioration in sound insulation. If the material of the mass portion 4b is resin, the resin may be made from a biomass material.

[0037] The spring constant (rigidity) of the spring portion 4 a is determined based on the mass of the mass portion 4 b so that the resonant frequency coincides with the frequency that is the main target of sound insulation. For example, if the mass of the mass portion 4 b is 1.0 g and the main target frequency of sound insulation is 1000 Hz or less, the spring constant of the spring portion 4 a 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 lightweight, and the dimensions in the direction perpendicular to the film portion 2 are relatively small. As described above, 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 both a flat mounting surface and a curved or uneven mounting surface, without the need for fixing by adhesive or the like.

[0039] FIG. 3A is a perspective view of a sound-insulating structure 1 according to a modification of the first embodiment of the present invention, and FIG. 3B is a cross-sectional view taken along line A-A in FIG. 3A and inverted. FIG. 4A is a cross-sectional view of a sound-insulating structure 1 according to another modification, and FIG. 4B is a perspective view of the weight portion 4 of that sound-insulating structure 1. FIG. 5A is a cross-sectional view of a sound-insulating structure 1 according to yet another modification, and FIG. 5B is a perspective view of the weight portion 4 of that sound-insulating structure 1. In these modifications, the spring portion 4a and the mass portion 4b of the weight portion 4 have different shapes and dimensions. In the modifications shown in FIGS. 3A and 3B, the spring portion 4a is cylindrical with a small diameter, and the mass portion 4b is cylindrical with a large diameter. In the modifications shown in FIGS. 4A and 4B, the spring portion 4a is elongated and cylindrical, the mass portion 4b is spherical, 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 Figures 5A and 5B, the spring portion 4a is frustoconical, and the mass portion 4b is cylindrical. The diameter of the smallest part of the frustoconical spring portion 4a is substantially the same as the diameter of the cylindrical mass portion 4b. In the modified example shown in Figures 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, thereby forming a spring-mass resonator. 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 Figures 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 with a higher density than the spring portion 4a, and the mass portion 4b has a larger mass than the spring portion, thereby forming a spring-mass resonator. As shown in the modified example in Figures 5A and 5B, if the spring portion 4a is a truncated cone that tapers away from the membrane portion 2, the membrane portion 2 and the spring portion 4a can be easily released from the 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, to make the mass portion 4b larger in mass than the spring portion 4a, thereby forming a spring-mass resonator and achieving a sufficient sound-insulating effect. In other words, the materials, shapes, and dimensions of the spring portion 4a and the mass portion 4b are determined so as to form a spring-mass resonator that can provide a sufficient sound-insulating effect. As long as the mass portion 4b can be made larger in mass than the spring portion 4a to the extent that a spring-mass resonator that can provide a sufficient sound-insulating effect can be formed, the materials, shapes, and dimensions of the spring portion 4a and the mass portion 4b can be freely selected. However, the spring portion 4a must be made of a flexible material in order to function as a spring.

[0041] [Second Embodiment] Figure 6A is a perspective view of a sound-insulating structure 6 according to a second embodiment of the present invention, and Figure 6B is a cross-sectional view taken along line A-A in Figure 6A and inverted. The sound-insulating 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 membrane portion 2 functions as the spring portion. As an example, the mass of the weight portion 7 is approximately 0.1 g to 2.0 g. The material of the weight portion 7 is not limited, and it may be formed from, for example, synthetic resin or metal. The rest of the configuration is similar to that of the first embodiment, so a description thereof will be omitted. In the sound-insulating structure 6 according to this embodiment, membrane vibration is controlled by the action of the spring-mass resonator formed by the weight portion 7 and the membrane portion 2. This significantly reduces membrane vibration in a specific frequency range (e.g., below 1000 Hz), 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 part of the spring (air spring) of the spring mass resonator.

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

[0043] The support wall 3 of this embodiment is made of 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. Similarly, the membrane 2 of this embodiment is made of 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.

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

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

[0046] In the sound-insulating structures 1 and 6 described above, as shown in Figures 8A and 8B, the support wall 3 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, and the planar shape of each compartment 5 is square. In other words, the support wall 3 is a rectangular tube having a square cross-section that defines each compartment 5, and a large number of rectangular support walls 3 are arranged side by side, and the support walls 3 of adjacent compartments 5 are integrated. However, this configuration is not limited to this. For example, as shown in Figures 9A and 9B, the planar shape of each compartment 5 may be triangular, and the support wall 3 may be a rectangular tube having a triangular cross-section that defines each compartment 5. 10A and 10B, the planar shape of each compartment 5 may be pentagonal, and the support wall 3 may be a rectangular tube having a pentagonal cross-section defining each compartment 5. As shown in FIGS. 11A and 11B, the planar shape of each compartment 5 may be hexagonal, and the support wall 3 may be a rectangular tube having a hexagonal cross-section defining each compartment 5, forming a so-called honeycomb structure. Furthermore, as shown in FIGS. 12A and 12B, the planar shape of each compartment 5 may be circular, and the support wall 3 may be a cylindrical tube having a circular cross-section defining each compartment 5. In the configurations shown in FIGS. 10A, 10B, 12A, and 12B, gaps are formed between the compartments 5, so it is preferable to determine the shape and dimensions of the support wall 3 so as to minimize these gaps. In the configurations shown in FIGS. 8A, 8B, 9A, 9B, 11A, and 11B, no gaps are formed between the compartments 5. Furthermore, each compartment 5 may have various shapes (not shown), such as a rectangle, a parallelogram, a trapezoid, a polygon with 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-insulating structures 1, 6 of the present invention are very thin and lightweight, and can be easily placed on curved or uneven surfaces. Therefore, they may be placed on the panels of vehicles, particularly automobiles. Automobile panels are generally non-porous plates, such as metal plates (iron plates, steel plates, aluminum plates) and resin plates. When the panel on which the sound-insulating structure 1 is placed is a metal plate, its thickness is preferably in the range of 0.5 mm to 2.0 mm. When the panel is a resin plate, its thickness is preferably in the range of 0.5 mm to 20 mm. When the sound-insulating structures 1, 6 are placed on the panel of an automobile, it is preferable that the end face of the support wall 3 of the sound-insulating structures 1, 6 opposite the side attached to the membrane 2 is placed on the panel. In this case, the support wall 3 and the panel may or may not be bonded to each other. However, it is preferable that the support wall 3 be placed on the panel without being bonded to the panel.

[0048] Furthermore, the sound-insulating structures 1, 6 of the present invention may be used alone or in combination with other members (not shown). When the sound-insulating structures 1, 6 of the present invention are used in combination with other members, they may be laminated or joined to the other members. When laminated or joined to other members, the sound-insulating structures 1, 6 may be placed so that they come into contact with the portion on which the sound-insulating structures 1, 6 are placed (e.g., an automobile panel), or the other member may be placed so that the other member comes into contact with that portion. The other members used in combination with the sound-insulating structures 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, an engine head cover, an engine body cover, a hood insulator, a front-dash insulator, an air box wall, an air intake cleaner, a dust side duct, and an undercover; in the cabin, examples include a dash insulator, a dash panel, a floor carpet (floor silencer), a spacer, door trim, the inside of the door trim, an instrument panel, an instrument center box, an instrument upper box, an air conditioner housing, a roof trim, the inside of the roof trim, a sun visor, an air conditioning duct for a rear seat, a cooling duct of a battery cooling system in a battery-equipped vehicle, a cooling fan, a center console trim, the inside of the console, a parcel trim, a parcel panel, a seat headrest, a front seat back, and a rear seat back; and in the trunk, examples include a trunk side trim, the inside of the trim, and a drafter cover. Furthermore, the sound-insulating structures 1, 6 of the present invention can be installed inside the frame of an automobile or between panels, and can also be installed outside the automobile in under-floor covers, fender protectors, back doors, wheel covers, aerodynamic covers for suspensions, and the like.

[0050] Specific examples and comparative examples of the sound-insulating structure of the present invention are described below. [Example 1] The sound-insulating structure 1 of Example 1 of the present invention has the same structure as 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 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 film portion 2 of this example has 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 portion 2 has an area of ​​1000 cm. 2 When the square is 1, the bending stiffness K is 67.2 N / mm 2 The planar shape has an area of ​​400 cm 2 When the square shape is 100 mm, the bending stiffness K is 42.5 N / mm 2 If the same material as the film portion 2 is used, the film thickness is 3 mm, and the plane shape has an area of ​​1000 cm 2 When a square membrane portion is formed, its bending stiffness K is about 1.5×10 4 N / mm 2 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 (tanδ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the support wall portion 3 of 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 according to JIS K6253 of 65, a plate thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the membrane portion 2. However, only the outermost support wall portion 3 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 49 compartments 5 exist in the 200 mm x 200 mm square area (evaluation surface) of the membrane 2. However, only a portion of this area is shown in the drawing. 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 this 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 at frequencies of 1 Hz to 1000 Hz, and a loss tangent (tanδ) of 0.01 or more and 0.50 or less at 23°C and at frequencies 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 the side attached to the membrane portion 2, also has a height of 3 mm and is made of rigid stainless steel (SUS304). The mass of the weight 4 is approximately 0.8 g, and has a resonance frequency that shows a peak at 600 Hz to 650 Hz in the direction perpendicular to the installation surface of the weight 4. The height of the entire sound-insulating structure 1 is 10.5 mm, and the overall surface density of one section 5, including the film 2, support wall 3, and weight 4, is 2.97 kg / m 2 is.

[0053] As shown in FIG. 13 , the end face of the support wall 3 of the sound-insulating structure 1 opposite the side attached to the membrane 2 was placed on a 0.8 mm-thick steel plate 8, and sound insulation was measured with the surface of the steel plate 8 opposite the side on which the sound-insulating structure 1 was placed as the incident sound side. Specifically, in accordance with the intensity method specified in JIS A1441-1, a test facility room with a reverberation chamber as the sound source room and a semi-anechoic chamber as the sound receiving room was used, and sound transmission loss (transmission loss) [dB] was calculated for each 1 / 3 octave band center frequency [Hz] by 1 / 3 octave band analysis. The relationship between the 1 / 3 octave band center frequency and sound transmission loss was calculated and is shown in FIGS. 14A to 14F and 14K. The larger the sound transmission loss, the higher the sound insulation. Note that in the 1 / 3 octave band center frequencies [Hz] shown in FIGS. 14A to 14K, 1 kHz corresponds to 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 in which no sound insulation structure is provided. The surface density of this structure is 6.02 kg / m 2 is.

[0055] [Comparative Example 2] In Comparative Example 2, a member having the same mass as the sound-insulating structure 1 of Example 1 was placed on a 0.8 mm thick iron plate 8. The theoretical sound-insulating value calculated based on the mass law was obtained, and the relationship between the ⅓ octave band center frequency and the sound transmission loss is shown in Figure 14A. The surface density of this structure was 8.99 kg / m 2 is.

[0056] [Comparative Example 3] As Comparative Example 3, as shown in Figures 16A and 16B, a sound insulation structure consisting only of a film portion 2 and a supporting wall portion 3 was placed on a 0.8 mm thick iron plate 8, and sound insulation was measured. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Figures 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 is.

[0057] Example 2 A sound-insulating structure 6 according to 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 support 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 approximately 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 support wall 3 of the sound-insulating structure 6 opposite to the side attached to the film 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 of Example 3 of the present invention shown in Figures 18A and 18B has the same structure as Example 2, but has a weight 7 that is smaller than the weight 7 of Example 2. The film 2 and support wall 3 of this example are the same as the film 2 and support wall 3 of Example 1. The weight 7 is made of EPDM with 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 2) of 5 mm. The mass of the weight 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 support 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-insulating structure 1 (not shown) of Example 4 of the present invention has the same structure as Example 1, but has a support wall portion 3 that is softer than the support 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 support 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 support wall portion 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 according to JIS K6253-3 of 30, a plate thickness of 1.6 mm, and a height of 10 mm in the direction perpendicular to the membrane portion 2. However, only the outermost support wall portion 3 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG. 14C.

[0060] Comparative Example 4 The sound-insulating structure (not shown) of Comparative Example 4 has substantially the same structure as that of Example 1, but has a support wall portion 3 that is harder and less flexible than the support wall portion 3 of Example 1. The film portion 2 and weight portion 4 of this comparative example are the same as the film portion 2 and 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 areal 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG. 14C.

[0061] Example 5 A sound-insulating structure 1 (not shown) of Example 5 has the same structure as Example 1, but includes a film portion 2 that is softer than the film portion 2 of Example 1. The support wall portion 3 and weight portion 4 of this example are the same as the support 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, the same material as the support 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0062] 19A and 19B has the same structure as that of Example 1, but has compartments 5 that are wider than those of Example 1. The film portion 2 and weight portion 4 of this example are the same as those of Example 1. The support wall portions 3 of this example are the same as those of Example 1, but are arranged at wider intervals than those of Example 1. As a result, each compartment 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 compartments 5 in a 200 mm x 200 mm square area (evaluation surface) of the membrane 2. However, only a portion of this area is shown in the drawing. As shown in Figure 19B, the end face of the support wall 3 of the sound-insulating structure opposite the side attached to the membrane 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in Figure 14E.

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

[0064] The membrane portion 2 and the support wall portion 3 of this embodiment are the same as the membrane portion 2 and the support wall portion 3 of Example 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0065] Example 8 The sound-insulating 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 support wall portion 3 of this example are the same as those of Example 1, but the weight portion 4 of this example consists of a small-diameter, cylindrical spring portion 4a and a large-diameter, cylindrical mass portion 4b. The spring portion 4a, which is the portion of the weight portion 4 attached to the film portion 2, is cylindrical with a diameter of 6 mm and a height (dimension perpendicular to the film portion 2) of 3 mm and is made of the same material as the spring portion 4a of the weight portion 4 of Example 1 (silicone rubber with a durometer A hardness of 10 according to JIS K6253-3). The mass portion 4b, which is the portion of the weight portion 4 opposite 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation properties were measured, and the results are 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 with 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation properties were measured, and the results are shown in Figures 14G to 14I.

[0067] [Example 10] The sound insulation structure 1 of Example 10 shown in Figure 20 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 9, but the support wall portion 3 of this example is made of EPDM with 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0068] Example 11 The sound-insulating 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-insulating structure 1, and Figure 21B is a cross-sectional view taken along line B-B. 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 of the multiple support wall portions have a height extending in a direction perpendicular to the film portion 2 that is greater than the other support wall portions 3c. In other words, the sound-insulating structure 1 of this example has support wall portions (some support wall portions) 3d that are as high in height as the support wall portions 3 of Example 10, and support wall portions (other support wall portions) 3c that are as low in height as the support wall portions 3 of Example 9. Specifically, the support wall portion 3c is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the membrane portion 2, while the support wall portion 3d is made of EPDM having a durometer A hardness of 30 according to JIS K6253, a thickness of 1.6 mm, and a height of 15 mm in a direction perpendicular to the membrane portion 2. The support wall portion 3d has a height 1.5 times that of the support wall portion 3c. In this embodiment, as shown in Figures 21A and 21B, rows containing high-height support wall portions 3d and rows containing only low-height support wall portions 3c are alternately positioned. As a result, of the 49 square compartments 5 arranged in a 7x7 grid, 16 compartments 5 are surrounded by high-height support wall portions 3d. The surface density of this configuration is 3.02 kg / m 2The end face of the support 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 performance was measured, and the results are shown in FIG.

[0069] Example 12 The sound-insulating structure 1 (not shown) of Example 12 has the same structure as the modified example of the first embodiment shown in Figures 3A and 3B. The weight portion 4 of this example is the same as the weight portion 4 of Example 8. The film portion 2 and the supporting wall portion 3 of this example have 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, and satisfy the JIS The durometer A hardness according to K6253 is 50, the thickness of the membrane 2 is 1.0 mm, the thickness of the support wall 3 is 1.2 mm, and the height in the direction perpendicular to the membrane 2 is 10 mm. The surface density of this structure 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0070] Example 13 The sound-insulating 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 support wall portion 3 of this example are the same as the film portion 2 and the support 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 having 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0071] Example 14 The sound-insulating 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 membrane 2 and support wall 3 of this example are the same as those of Example 12. The weight 4 of this example consists of a small-diameter cylindrical spring 4a and a large-diameter cylindrical mass 4b. The spring 4a, which is the part of the weight 4 attached to the membrane 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane 2) of 3 mm. The mass 4b, which is the part of the weight 4 opposite to the side attached to the membrane 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG.

[0072] [Comparative Example 5] In Comparative Example 5, similar to Comparative Example 3, a sound insulation structure consisting only of a film portion 2 and a support wall portion 3 was placed on a 0.8 mm thick iron plate 8 as shown in Figures 16A and 16B, and sound insulation was measured. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Figure 14J. The film portion 2 and support wall portion 3 of this example are different from the film portion 2 and support wall portion 3 of Example 1 and Comparative Example 3, but are the same as the film portion 2 and support 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 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 includes a film 2 made of a resin material with a thinner film thickness than that of Example 1. The support wall 3 and weight 4 of this example are the same as those of Example 1. The film 2 of this comparative example is made of low-density polyethylene (LDPE) with a film 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 an iron plate 8 having a thickness of 0.8 mm, and the sound insulation property was measured, and the result is shown in FIG. 14K.

[0074] [Results] The results of comparing the above-described Examples 1 to 14 of the present invention with Comparative Examples 1 to 6 will now be described. Referring to Fig. 14A, it can be seen that the sound-insulating effect is improved by the sound-insulating structure 1 of the present invention. In particular, the sound-insulating structure 1 of Example 1 provides a sound-insulating 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, which has the weight portion 4, has greater sound-insulating properties than Comparative Example 3, particularly in the frequency band lower than 1.25 kHz.

[0075] 14B , it can be seen that the sound-insulating structure 1 (Example 1) of the first embodiment of the present invention and the sound-insulating structure 6 (Examples 2 and 3) of the second embodiment of the present invention both achieve excellent sound-insulating effects. When the mass 4 itself constitutes a spring-mass resonator, as in Example 1, particularly excellent sound-insulating properties are obtained near frequencies (e.g., 630 Hz to 1000 Hz) where the vibration of the membrane 2 is reduced by the resonance of the spring-mass resonator. On the other hand, when the spring-mass resonator is formed by the mass 7 and the membrane 2, as in Examples 2 and 3, the frequency band where sound-insulating properties are particularly excellent can be adjusted by adjusting the weight of the mass 7. For example, if the mass of the mass 7 is approximately the same as that of the mass 4 of Example 1, the frequency band where sound-insulating properties are particularly excellent is around 1000 Hz. By reducing the weight of the mass 7, the frequency band where sound-insulating properties are particularly excellent can be shifted to a higher frequency.

[0076] 14C , it can be seen that if the support wall 3 of the sound-insulating structure is not made of a flexible material, the sound-insulating effect is poor, but if the support wall 3 is made of a flexible material, a good sound-insulating 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 membrane 2 via 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 membrane 2 via the support wall 3. Note that the frequency band in which sound-insulating properties are 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-insulating properties are particularly good can be shifted to a lower frequency side.

[0077] 14D, it can be seen that if the film portion 2 of the sound-insulating structure is too soft, the sound-insulating properties will be slightly reduced. This is thought to be because if the film portion 2 is too soft, vibrations of a degree sufficient for the spring-mass resonator to function properly will not be transmitted to the spring-mass resonator.

[0078] Referring to Figure 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-insulating structure is too large, the sound-insulating properties will be slightly reduced. This is thought to be because if each section 5 is too large, the spring mass resonator will not function sufficiently, and the vibration reduction effect will be reduced. Therefore, each section 5 should be made small to some extent (for example, 1000 mm 2 ) is preferred.

[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 ranges, the sound-insulating function of the present invention will be exhibited. Therefore, it can be seen that the material and shape of the weight 4, etc. can be freely set within the preferred ranges.

[0080] 14G, it can be seen that a similar sound-insulating effect can be obtained even if the durometer A hardness according to JIS K6253-3 of the support wall portion 3 differs to some extent. And, referring to FIG. 14H, it can be seen that a good sound-insulating effect can be obtained by configuring the support wall portion 3 so that it is tall in the direction perpendicular to the film portion 2. This is because, when the support wall portion 3 is tall, the thickness of the air layer located between the film portion 2 and the support surface (the steel plate 8 in each embodiment) on which the sound-insulating structures 1 and 6 are placed is large, which changes the frequency band of air resonance transmission, reducing the impact of sound-insulating interference in the target frequency band and increasing sound insulation, particularly in the low-frequency range (for example, around 500 Hz).

[0081] Referring to Figure 14I, it can be seen that a good sound insulation effect can be obtained even when only some of the support walls 3d among the multiple support walls are increased in height in the direction perpendicular to the membrane 2, while the heights of the other support walls 3c are decreased. Even when only some of the support walls 3d are increased in height, the thickness of the air layer between the support surface (the steel plate 8 in each embodiment) on which the sound insulation structure 1, 6 is placed and the membrane 2 is increased, just as in the case of a configuration in which all of the support walls 3d are increased in height. As a result, the sound insulation performance is particularly high in the low-frequency range (e.g., around 500 Hz), as described above. Furthermore, by increasing the height of only some of the support walls 3d, the thickness of the air layer is increased while suppressing an increase in the overall weight of the sound insulation structure 1, 6. This makes it easy to stably mount the sound insulation structure 1, 6 on support surfaces of various shapes, including curved surfaces. In other words, a lightweight sound insulation structure 1, 6 with good sound insulation performance in the low-frequency range can be provided. If there are too few high support walls 3d, it becomes difficult to stably support the sound insulation structures 1, 6, and if there are too many, the weight of the entire sound insulation structures 1, 6 increases. Therefore, it is preferable that the compartments 5 surrounded by the high support walls 3d account for 5% or more of the total compartments 5 of the sound insulation structures 1, 6. Furthermore, when viewing a cross section of each support wall 3c, 3d parallel to the membrane 2, it is preferable that the total cross-sectional area of ​​the high support walls 3d is 10% or more of the total cross-sectional area of ​​all the support walls 3c, 3d of the sound insulation structures 1, 6. In Example 11, a 20 mm x 20 mm (area 400 cm) portion of the membrane 2, which has a square planar shape of 25 mm x 25 mm, is enclosed by the high support walls 3d. 2) area, 7 × 7 = 49 compartments 5 are provided as shown in FIG. 21A, and 16 of these compartments 5 are compartments 5 surrounded by high support wall portions 3d, which is a preferable ratio of 32.6%.

[0082] In addition, 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 mentioned above, in order to prevent an increase in the overall weight of the sound-insulating structures 1, 6 and to prevent installation restrictions.

[0083] Referring to Figure 14J, it can be seen that even if the membrane portion 2 and the support wall portion 3 are formed by integral molding of a thermoplastic material, the provision of the weight portion 4 provides good sound insulation. In a spring-mass resonator consisting of the spring portion 4a and the mass portion 4b of the weight portion 4, as in Example 13, if the spring portion 4a is softer, the resonant frequency shifts to the lower frequency side, and a greater sound insulation effect is obtained at the lower frequency side. In this way, by changing the configuration of the weight portion 4, it is possible to adjust the sound insulation frequency band. Furthermore, it can be seen that good sound insulation can be obtained even if the weight portion 4 is made of a single material, as in Example 14. Therefore, productivity can be improved by manufacturing the weight portion from a single material.

[0084] 14K, it can be seen that if the membrane 2 is made of a thin resin material (film), sound insulation performance will decrease, so it is preferable that the membrane 2 have 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 membrane 2 thinner. However, unless the membrane 2 has a certain thickness, it will be too soft, and vibrations sufficient to allow the spring-mass resonator consisting of the spring portion 4a and mass portion 4b of the weight portion 4 to function properly will not be transmitted to the weight portion 4. Therefore, it is preferable that the membrane 2 have a certain thickness.

[0085] [Soundproof Structure] A soundproof structure 11 will now be described, which includes the soundproof structures 1 and 6 of the present invention described above, has enhanced soundproofing properties, and is easier to install. First, FIG. 22 shows a side view of an automobile, which is an example of a vehicle equipped with the soundproof structure 11. The soundproof structure 11 of the present invention is disposed so as to overlap a panel (dash panel) 14 provided at the boundary between the engine compartment 12 and the 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 taken along line C-C of FIG. 24 is shown in FIG. 25. The soundproof structure 11 comprises a soundproof plate-like portion 10 and a soundproof structure portion 9 positioned side by side in a plane. The soundproof structure portion 9 has the same configuration as either of the soundproof structures 1 and 6 of the present invention described above. That is, the soundproof structure portion 9 comprises either 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 structure portions 9 are formed integrally or joined together to form a soundproof structure 11 that can be handled as a single component.

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

[0087] An example of the sound-insulating structure 9 has the same configuration as the sound-insulating structure 1 shown in FIGS. 1A to 2B . That is, the sound-insulating structure 9 is composed of the sound-insulating structure 1 of the present invention described above. This sound-insulating structure 9 includes an elastic sheet-like membrane 2, an elastic support wall 3 extending substantially perpendicularly from the membrane 2, and an elastic weight 4 extending substantially perpendicularly from the membrane 2. Each weight 4 located in each compartment 5 constitutes a spring-mass resonator having an elastic spring 4a and a mass 4b having a larger mass than the spring 4a. Because this sound-insulating structure 9 has the same configuration as the sound-insulating structure 1 shown in FIGS. 1A to 2B , as described above, the vibration of the membrane 2 is controlled by the action of the spring-mass resonator formed by the spring 4a and mass 4b of the weight 4. In particular, membrane vibration is significantly reduced in a specific frequency range (e.g., frequencies below 1000 Hz), providing high sound insulation.

[0088] In this soundproof structure 11, the soundproof structures 9 having the above-described configuration are disposed in areas of a vehicle where sound propagation is particularly strong. In the example shown in FIG. 22 , the soundproof structure 11 is disposed so as to overlap a panel 14 located at the boundary between an engine compartment 12 and a passenger compartment 13 of an automobile. The soundproof structures 9 are disposed at two locations facing the front tires, areas where road noise propagation is particularly strong. If the entire soundproof structure 11 disposed so as to overlap the panel 14 were composed of soundproof structures 9 having the above-described configuration, the soundproof structure 11 would have a high soundproofing effect, but its weight would be heavy, which could adversely affect the performance of the vehicle. In contrast, in the soundproof structure 11 of this embodiment, the soundproof structures 9 having a particularly high soundproofing effect are disposed in areas where sound propagation is strong (e.g., positions facing the tires), and soundproof plate-like members 10 having a simple configuration are disposed in areas where sound propagation is not so strong (positions other than positions facing the tires). This makes it possible to efficiently suppress sound penetration while minimizing the increase in weight. Furthermore, not only the soundproof plate-like portion 10 formed to fit 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 the need for fixing by adhesive or the like. Therefore, the soundproof structure 11 of this embodiment can be stacked on a 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 right in Figures 22 and 23 , and primarily shown in Figure 24 ), the area occupied by the soundproofing structure 9 is preferably 5% to 95% of the overall 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, will be insufficient. Furthermore, if the proportion of the area occupied by the soundproofing structure 9 is too large, noise propagating through the soundproofing structure 11 toward the vehicle interior is reflected by the instrument panel, hits a surface of the soundproofing structure 11 that is not laminated with sound-absorbing material, and is reflected again, resulting in an increase in sound pressure and a muffled sound. In the examples shown in Figures 22 to 25 , the area occupied by the soundproofing structure 9 is approximately 30% of the overall area of ​​the soundproofing structure 11.

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

[0091] The soundproof structure 11 of the present invention is suitable for use by being placed on a vehicle, particularly an automobile panel (e.g., panel 14 shown in Figures 1A-1B), because not only the soundproof plate portion 10 but also the soundproof structure portion 9, as described above, are very thin and lightweight and can be easily placed on a curved or uneven surface. 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, position, and usage of the soundproof structure 11 may be the same as the arrangement, position, and usage 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 Examples 1 to 14 described above, and additionally includes a soundproof plate part 10. Therefore, it can be said that the difference in sound insulation properties between the soundproof structures 1 and 6 of Examples 1 to 14 represents the difference in sound insulation properties between the soundproof structures 11. Furthermore, as described above, the soundproof structures 1 and 6 of Examples 1 to 14 have greater sound insulation properties than the structures of Comparative Examples 1 to 6. In addition, the soundproof structure 11 of the present invention is considered to exhibit even better sound insulation properties by virtue of the inclusion of the soundproof plate part 10.

[0093] The present invention includes the following configurations and methods: [1] A sound-insulating structure comprising: an elastic membrane; an elastic support wall extending upright from the membrane; and a weight extending upright from the membrane, wherein the membrane is divided into a plurality of compartments by the support wall, and the weight is located in each of the compartments or in some of the compartments, and each of the compartments having a weight located therein has one weight disposed therein, wherein the height of the support wall extending in a direction perpendicular to the membrane is greater than the height of the weight extending in the direction perpendicular to the membrane, and each of the weights constitutes a spring-mass resonator having an elastic spring and a mass having a mass greater than that of the spring. [2] The sound-insulating structure according to [1], wherein the membrane, the support wall, and the spring are all made of a material having rubber elasticity but no energy elasticity, a material having energy elasticity but no rubber elasticity, or a material having both rubber elasticity and energy elasticity. [3] The sound-insulating structure according to [1] or [2], 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] The sound-insulating structure according to any one of [1] to [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 at a frequency of 1 Hz to 1000 Hz. [5] The sound-insulating structure according to any one of [1] to [4], wherein the spring portion of the weight portion is located on the side of the weight portion attached to the film portion, and the mass portion is located on the side of the weight portion opposite to the side attached to the film portion. [6] The sound-insulating 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] The sound-insulating structure according to any one of [1] to [6], wherein the mass portion of the weight portion is made of a material with a higher density than the spring portion.[8] A sound-insulating structure comprising: an elastic membrane portion; an elastic support wall portion standing on the membrane portion; and a weight portion standing on the membrane portion, wherein the membrane portion is divided into a plurality of compartments by the support wall portion, and a weight portion is located inside each of the plurality of compartments or inside some of the plurality of compartments, and each of the weight portions is located in one of the compartments in which the weight portion is located, and 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 the direction perpendicular to the membrane portion, and wherein the membrane portion functions as a spring portion and the weight portion functions as a mass portion, thereby constituting a spring-mass resonator. [9] The sound-insulating structure according to [8], wherein both the membrane portion and the support wall portion are made of a material that has rubber elasticity but no energy elasticity, a material that has energy elasticity but no rubber elasticity, or a material that has both rubber elasticity and energy elasticity.

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

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

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

[12] The sound-insulating structure according to any of [1] to

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

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

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

[14] The area of ​​each of the compartments is 100 mm. 2 More than 1000mm 2

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

[13] , wherein the area of ​​the film portion is 1000 cm or less. 2

[16] The sound-insulating structure according to any one of [1] to

[14] , wherein 10 to 1000 of the compartments are provided per 1000 cm2 of the film portion. 2

[15] The sound-insulating structure according to

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

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

[16] , wherein the plate thickness of the support wall portion is 0.5 mm to 5.0 mm.

[18] The sound-insulating structure according to

[17] , wherein the plate thickness of the support wall portion is 1.0 mm to 3.0 mm.

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

[18] , wherein the film thickness is 0.1 mm to 3.0 mm.

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

[19] , wherein the height in a direction perpendicular to the film portion is 5 mm to 20 mm.

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

[20] , wherein the height of the support wall portion extending in a direction perpendicular to the film portion is 5 mm to 20 mm.

[22] The sound-insulating structure according to

[21] , wherein the height of the support wall portion extending in a direction perpendicular to the film portion is 10 mm to 20 mm.

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

[22] , which has a plurality of the support wall portions, and some of the support wall portions have a height extending in a direction perpendicular to the film portion greater than that of the other support wall portions.

[24] The sound-insulating structure according to

[23] , wherein the height of the support wall portion that is taller extending in a direction perpendicular to the film 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] The sound-insulating structure according to any one of [1] to

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

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

[25] , wherein the film portion has a durometer A hardness of 30 or greater, and the support wall portion has a durometer A hardness of 1 or greater and 90 or less.

[27] A soundproof structure comprising a soundproof plate-shaped portion and a sound-insulating structural portion, wherein the soundproof plate-shaped portion is a plate-shaped member made of a sound-absorbing or sound-insulating material, and the sound-insulating structural portion is the sound-insulating structure according to any one of [1] to

[26] , and wherein at least one of the membrane portion and the support plate portion and the sound-insulating plate-shaped portion are integrally formed or joined to each other, and the sound-insulating plate-shaped portion and the sound-insulating structural portion are positioned side by side in a plane.

[28] The soundproof structure according to

[27] , wherein an area of ​​a main surface of the soundproof structure occupied by the sound-insulating structural portion is 5% to 95% of the area of ​​the entire soundproof structure.

[29] The soundproof structure according to

[27] or

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

[30] The soundproof structure according to any of

[27] to

[29] , wherein the soundproof plate-like 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] The soundproof structure according to any of

[27] to

[30] , which is attached to a panel inside a vehicle.

[32] The soundproof structure according to

[31] , which is attached to a dash panel of a vehicle, and wherein the soundproof structure portions are provided in positions facing the tires.

[0094] REFERENCE SIGNS LIST 1, 6 Sound insulation structure 2 Membrane portion 3 Support wall portion 3a First wall portion 3b Second wall portion 3c Low height support wall portion (other support wall portion) 3d High height support wall portion (part of support wall portion) 4, 7 Weight portion 4a Spring portion 4b Mass portion 5 Compartment 8 Iron plate 9 Sound insulation structure portion 10 Soundproof plate-shaped portion 11 Soundproof structure 12 Engine room 13 Vehicle interior 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.