Sound insulation structure

Abstract

To provide a thin and lightweight sound insulation structure that provides sufficient sound insulation and can be easily and stably placed on a curved mounting surface.SOLUTION: A sound insulation structure 1 has: a membrane portion 2 having elasticity; a support wall portion 3 standing on the membrane portion 2 and having elasticity; a weight portion 4 standing on the membrane portion 2; and a hard layer 10 laminated on the opposite side of the support wall portion 3 and the weight portion 4 of the membrane portion 2. The membrane portion 2 is divided into a plurality of compartments 5 by the support wall portion 3, and the weight parts 4 are each located inside all or some of the plurality of compartments 5, with one weight section 4 located in one compartment 5. A height H1 of the support wall portion 3 in a direction orthogonal to the membrane portion 2 is greater than a height H2 of the weight portion 4 in the direction orthogonal to the membrane portion 2. Each of the weight portions 4 constitutes a spring mass resonator having a spring portion 4a having elasticity and a mass portion 4b having a greater mass than the spring portion 4a. The hard layer 10 comprises a membrane having a thickness of 1 μm or more and 3,000 μm or less and harder than the membrane portion 2.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a sound insulation structure. [Background technology]

[0002] In recent years, in the rooms of buildings such as apartment buildings, office buildings, and hotels, outdoor noise from automobiles, trains, airplanes, ships, etc. outside the building, and equipment noise and human voices generated outside the room in the building are required to be blocked, and quietness suitable for the use of the room is required. In addition, in the interior of vehicles such as automobiles, trains, airplanes, and ships, it is desired to reduce noise in order to block wind noise and engine noise and provide a quiet and comfortable space for the occupants. Therefore, there is a demand for a means for blocking the propagation of noise and vibration from the outside to the inside of a building or vehicle, and also for the propagation of noise and vibration from the outside to the inside of a building or vehicle, that is, a member with high sound insulation properties. In recent years, there is a demand for lightweight sound insulation members in buildings due to the increase in height, and there is also a demand for lightweight sound insulation members in vehicles to improve energy efficiency. Examples of sound insulation structures forming soundproof walls in vehicles and buildings are disclosed in Patent Documents 1 to 4.

[0003] The invention described in Patent Document 1 comprises an acoustic damping panel comprising a rigid frame divided into a number of individual cells, a sheet of flexible material, and a number of weights, each weight being fixed to the sheet of flexible material such that each cell is provided with its own weight, and the attenuated sound is controlled by appropriate selection of the mass of the weights.

[0004] In the invention described in Patent Document 2, in a soundproofing material having an elastic sheet and a support part that holds the sheet and divides the sheet into partitions, the relationship between the rigidity of the sheet in the partitions and the areal density of the sheet is specified.

[0005] The soundproofing material of the invention described in Patent Document 3 is a structure comprising a flat substrate portion and a plurality of resonating portions connected to the substrate portion and having a predetermined resonant frequency, each of the plurality of resonating portions having a weight portion and a connecting portion connecting the weight portion to the substrate portion, and configured such that in a projection view viewed from a direction perpendicular to the substrate portion, the center of gravity of the resonating portion is located outside the joint area between the substrate portion and the connecting portion.

[0006] The vibration reduction device of the invention described in Patent Document 4 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. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] JP 2005-250474 A [Patent Document 2] International Publication No. 2019 / 022245 [Patent Document 3] JP 2021-152584 A [Patent Document 4] JP 2020-91481 A Summary of the Invention [Problem to be solved by the invention]

[0008] The sound-damping panel described in Patent Document 1 has a rigid frame that is not flexible, and vibrations are transmitted to the seat via this rigid frame, so there is a risk that sufficient sound insulation cannot be obtained. In addition, if the surface on which the rigid frame is placed is curved or uneven, the sound-damping panel may not be stably held. In particular, since the panels of general vehicles (e.g., automobiles) have many curved or uneven parts, it is difficult to simply use the sound-damping panel of Patent Document 1 as a sound-insulating material for vehicles. In addition, the rigid frame has a large mass, and the increase in mass due to the sound-insulating material in the vehicle may be a problem.

[0009] The soundproofing material described in Patent Document 2 has a high support part, i.e., a high height extending from the seat in a direction perpendicular to the seat, and is preferably 25 mm or more. In order to stably support the seat with such a high support part, it is preferable that the support part has rigidity. As a result, there is a risk that sufficient sound insulation cannot be obtained because vibrations are transmitted through the support part, and it is difficult to place the soundproofing material on a curved or uneven placement surface such as a panel of a vehicle (e.g., an automobile). In addition, such a high support part leads to an increase in size and weight of the entire soundproofing material, and when placed on a panel of a vehicle, the soundproofing material occupies a large space inside the vehicle, reducing space efficiency, and there is a concern that it will hinder the installation of other components and get in the way of occupants.

[0010] In the sound insulation material described in Patent Document 3, the resonating part, which is the functional part that exerts the sound insulation effect, is exposed and not covered by a supporting wall, etc., and there is a risk that the sound insulation performance will decrease or change if this resonating part comes into contact with other members or the human body. Therefore, it is necessary to provide a large space around the resonating part, which reduces the space efficiency.

[0011] The vibration reduction device described in Patent Document 4 does not have a membrane part, but is composed of a plurality of vibrators and a frame connecting them. Therefore, like the sound insulation material of Patent Document 3, the vibrator, which is a functional part that exerts a sound insulation effect, is exposed, and if this vibrator comes into contact with other members or the human body, the sound insulation may be reduced or changed. In addition, in order to ensure the minimum structural strength of the vibration reduction device, the frame is required to have rigidity. As a result, there is a risk that sufficient sound insulation cannot be obtained because vibration is transmitted through the frame, and it is difficult to place the vibration reduction device of Patent Document 4 on a curved or uneven mounting surface such as a panel of a vehicle (e.g., an automobile).

[0012] Therefore, an object of the present invention is to provide a thin and lightweight sound insulation structure that can provide sufficient sound insulation and can be easily and stably placed on a curved or uneven support surface such as the panel of a building, mechanical device, or vehicle (e.g., an automobile), and that has good sound insulation properties, particularly in the low frequency range of 1000 Hz or less. [Means for solving the problem]

[0013] The sound-proofing structure of the present invention comprises an elastic membrane portion, an elastic support wall portion standing on the membrane portion, a weight portion standing on the membrane portion, and a hard layer laminated on the surface of the membrane portion opposite the surface on which the support wall portion and the weight portion are provided, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located inside all of the plurality of compartments or inside some of the plurality of compartments, and in the compartment in which the weight portion is located, one weight portion is disposed in one of the compartments, the height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than the height of the weight portion extending in a direction perpendicular to the membrane portion, each of the weight portions constitutes a spring mass resonator having an elastic spring portion and a mass portion having a mass greater than that of the spring portion, and the hard layer is made of a film having a thickness of 1 μm or more and 3000 μm or less and harder than the membrane portion. The term "elasticity" used here refers to the property of a solid substance that has been deformed by an external force returning to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, a substance is said to have "elasticity" when it has at least one of energy elasticity and rubber elasticity (entropy elasticity). The support wall and the spring may be made of any of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane may be made of any of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. The film portion, the supporting wall portion, and the spring portion may all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. The film portion, the supporting wall portion, and the spring portion may all be made of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. Specifically, the elasticity of the film part, the supporting wall part, and the spring part is evaluated by a dynamic storage modulus (E') obtained by measuring frequency dependency in tension or compression mode with a dynamic viscoelasticity measuring device in accordance with JIS K7244 and obtaining a master curve based on 23° C., and the dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less. More preferably, both the film part and the supporting wall part may be made of an elastic body having a dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 MPa or more and 50 MPa or less, and a loss tangent at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 or more and 0.45 or less. The spring portion of the weight may be located on a side of the weight that is attached to the membrane portion, and the mass portion may be located on a side of the weight that is opposite to the side that is attached to the membrane portion. The mass portion of the weight portion may have a larger volume than the spring portion. The mass portion of the weight portion may be made of a material having a higher density than the spring portion.

[0014] Another sound-proofing structure of the present invention comprises an elastic membrane portion, an elastic supporting wall portion standing on the membrane portion, a weight portion standing on the membrane portion, and a hard layer laminated on the surface of the membrane portion opposite the surface on which the support wall portion and the weight portion are provided, the membrane portion is divided into a plurality of compartments by the supporting wall portion, the weight portion is located inside all of the plurality of compartments or inside some of the plurality of compartments, and in the compartment in which the weight portion is located, one weight portion is disposed in one of the compartments, the height of the supporting wall portion extending in a direction perpendicular to the membrane portion is greater than the height of the weight portion extending in a direction perpendicular to the membrane portion, the membrane portion serves as a spring portion and the weight portion serves as a mass portion to constitute a spring-mass resonator, and the hard layer is made of a film having a thickness of 1 μm or more and 3000 μm or less and harder than the membrane portion. The support wall portion may be made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane portion may be made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Both the film part and the supporting wall part may 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. Also, both the film part and the supporting wall part may be made of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. More preferably, both the film part and the supporting wall part 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 at a frequency of 1 Hz to 1000 Hz, and a loss tangent of 0.05 or more and 0.45 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz.

[0015] The sound insulating structure and the other sound insulating structure of the present invention may have the following configuration. The hard layer may have a dynamic storage modulus at 23° C. and a frequency of 1 Hz to 1000 Hz of 1 MPa or more and 100 GPa or less. The support wall portion may include a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending in a first direction parallel to the membrane portion, and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and extending in a second direction perpendicular to the first direction. The support wall portion may be cylindrical having a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or may be rectangular tubular having a polygonal cross-sectional shape that defines each of the compartments, specifically a square, regular pentagon or regular hexagon. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 It may be the following: The area of ​​the membrane is 1000 cm 2 There may be from 10 to 1000 such compartments per unit area, and more preferably from 50 to 500 such compartments per unit area. The plate thickness of the support wall portion may be 0.5 mm or more and 5.0 mm or less, and is more preferably 1.0 mm or more and 3.0 mm or less. The film thickness of the film portion may be 0.1 mm or more and 3.0 mm or less. The height in a direction perpendicular to the film portion may be 5 mm or more and 20 mm or less. The height of the support wall in the direction perpendicular to the membrane may be 5 mm to 20 mm, and more preferably 10 mm to 20 mm. The support wall may have different heights in parts. The support wall may have a plurality of support walls, and some of the support walls may have a height extending in a direction perpendicular to the membrane portion greater than the other support walls. The height of the support wall that is taller extending in a direction perpendicular to the membrane portion may be greater than 10 mm and not greater than 20 mm, and the height of the other support walls (the support wall that is shorter) may be not greater than 10 mm. The support wall that is taller here refers to a support wall that is taller (for example, 1 mm or more) than the other support walls (the support wall that is shorter). The weight portion may have a height of 1 mm or more extending in a direction perpendicular to the film portion. The film portion may have a durometer A hardness of 30 or more, and the support wall portion may have a durometer A hardness of 1 or more and 90 or less. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3. Effect of the Invention

[0016] According to the present invention, it is possible to provide a thin and lightweight soundproofing structure that has sufficient soundproofing properties and can be easily and stably placed on a curved or uneven support surface such as the panel of a building, mechanical device, or vehicle (e.g., an automobile), and that has particularly good soundproofing properties in the low frequency range of 1000 Hz or less. [Brief description of the drawings]

[0017] [Figure 1] FIG. 2A is a perspective view of a sound-proofing structure according to a first embodiment of the present invention, and FIG. 2B is a cross-sectional view taken along line AA thereof. [Diagram 2] FIG. 2(A) is an exploded perspective view of one section of the sound-proofing structure shown in FIG. 1, and FIG. 2(B) is an exploded front view thereof. [Diagram 3] 1A is a perspective view of a sound-proofing structure according to a modified example of the first embodiment of the present invention, and FIG. 1B is a cross-sectional view taken along line AA thereof. [Figure 4] FIG. 1A is a cross-sectional view of a sound-insulating structure according to another modified example of the first embodiment of the present invention, and FIG. 1B is a perspective view of a weight portion of the sound-insulating structure. [Diagram 5]FIG. 1A is a cross-sectional view of a sound-insulating structure according to still another modified example of the first embodiment of the present invention, and FIG. 1B is a perspective view of a weight portion of the sound-insulating structure. [Figure 6] 5A is a perspective view of a sound insulation structure according to a second embodiment of the present invention, and FIG. 5B is a cross-sectional view taken along line AA thereof. [Figure 7] FIG. 13(A) is a cross-sectional view of a sound-insulating structure according to a modified example of the second embodiment of the present invention, and (B) is a perspective view of a weight part of the sound-insulating structure. [Figure 8] FIG. 1A is a plan view showing a schematic diagram of one section of a sound-insulating structure of the present invention, and FIG. 1B is a plan view showing a schematic diagram of a plurality of sections. [Figure 9] FIG. 2(A) is a plan view showing a schematic diagram of one section of another example of the sound-insulating structure of the present invention, and FIG. 2(B) is a plan view showing a schematic diagram of a plurality of sections. [Figure 10] FIG. 2(A) is a plan view that shows a schematic view of one section of still another example of a sound-insulating structure of the present invention, and FIG. 2(B) is a plan view that shows a schematic view of a plurality of sections. [Figure 11] FIG. 2(A) is a plan view that shows a schematic view of one section of still another example of a sound-insulating structure of the present invention, and FIG. 2(B) is a plan view that shows a schematic view of a plurality of sections. [Figure 12] FIG. 2(A) is a plan view that shows a schematic view of one section of still another example of a sound-insulating structure of the present invention, and FIG. 2(B) is a plan view that shows a schematic view of a plurality of sections. [Figure 13] FIG. 2 is a cross-sectional view showing a state in which the sound-proofing structure of the first embodiment of the present invention is attached to an iron plate. [Figure 14] Graphs (A) to (E) show the sound insulation properties of Examples 1 to 6 of the present invention and Comparative Examples 1 to 7. [Figure 15] FIG. 11 is a cross-sectional view showing a state in which a sound-proofing structure according to a fourth embodiment of the present invention is attached to an iron plate. [Figure 16] FIG. 11 is a cross-sectional view showing a state in which a sound-proofing structure according to a fifth embodiment of the present invention is attached to an iron plate. [Figure 17] FIG. 11 is a cross-sectional view of the structure of Comparative Example 2. [Figure 18]FIG. 1A is a perspective view of the structure of Comparative Example 3, and FIG. 1B is a cross-sectional view showing the sound-proof structure attached to an iron plate. [Figure 19] FIG. 11 is a cross-sectional view of the structure of Comparative Example 4. [Figure 20] FIG. 11 is a cross-sectional view showing a state in which the structure of Comparative Example 5 is attached to an iron plate. [Figure 21] FIG. 10(A) is a perspective view of the structure of Comparative Example 6, and FIG. 10(B) is a cross-sectional view showing the sound-insulating structure attached to an iron plate. [Figure 22] FIG. 11 is a cross-sectional view showing a state in which the structure of Comparative Example 7 is attached to an iron plate. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0018] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. [First embodiment] FIG. 1(A) is a perspective view of a sound insulation structure 1 according to a first embodiment of the present invention, and FIG. 1(B) is a cross-sectional view taken along line AA in FIG. 1(A) and turned upside down. The sound insulation structure 1 has an elastic sheet-like film portion 2, an elastic support wall portion 3 standing substantially vertically from the film portion 2, a weight portion 4 standing substantially vertically from the film portion 2, and a hard layer 10 laminated on the surface of the film portion 2 opposite to the surface on which the support wall portion 3 and the weight portion 4 are provided. The film portion 2 is divided into a plurality of sections (unit structures) 5 by the support wall portion 3. The weight portion 4 is located in each of all of the plurality of sections 5, or in some of the plurality of sections 5. In the section 5 in which the weight portion 4 is located, one weight portion 4 is located within one section 5. FIG. 2(A) is an exploded perspective view of one section 5 of the sound insulation structure 1, and FIG. 2(B) 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 case where at least one of energy elasticity and rubber elasticity (entropy elasticity) is present.

[0019] The support wall 3 of this embodiment includes a plurality of first walls 3a extending in a first direction D1 parallel to the membrane 2, and a plurality of second walls 3b extending in a second direction D2 perpendicular to the first direction D1. Specifically, the plurality of first walls 3a are arranged in parallel, and the plurality of second walls 3b are arranged in parallel, and the first walls 3a and the second walls 3b are integrated at the intersections. In this way, the plurality of first walls 3a and the plurality of second walls 3b form a lattice structure, and a plurality of compartments 5 having a square planar shape partitioned by the first walls 3a and the second walls 3b are arranged in a matrix shape. In other words, the support wall 3 has a structure in which a plurality of square tubes having a square cross-sectional shape that defines each compartment 5 are arranged. The support wall 3 is preferably made of a flexible material such as rubber, elastomer, or resin foam. The flexible material referred to here is any one of a material that has rubber elasticity but not energy elasticity, a material that has energy elasticity but not rubber elasticity, and a material that has both rubber elasticity and energy elasticity.

[0020] In the present embodiment, the part of the weight part 4 attached to the membrane part 2 is the spring part 4a, and the part opposite to the side attached to the membrane part 2 is the mass part 4b, which has a larger mass than the spring part 4a. In the example shown in Figs. 1(A) to 2(B), the spring part 4a and the mass part 4b have the same shape and the same dimensions, but are made of different materials. The spring part 4a is made of a flexible material, and the mass part 4b is made of a material with a higher density than the material constituting the spring part 4a. A spring mass resonator is configured in which the spring part 4a functions as a spring and the mass part 4b functions as a mass. In addition to the spring part 4a of the weight part 4, the membrane part 2 may also function as a part of the spring of the spring mass resonator. Furthermore, the air in the space surrounded by the membrane part 2 and the support wall part 3 may also function as a part of the spring of the spring mass resonator (air spring). It is preferable that the spring portion 4a is also made of a flexible material, i.e., 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.

[0021] The hard layer 10 of this embodiment is laminated on the surface of the film portion 2 opposite to the surface on which the support wall portion 3 and the weight portion 4 are provided, and is integrated with the film portion 2. The hard layer 10 is made of a film harder than the film portion 2. The thickness of the hard layer 10 is preferably 1 μm or more and 3000 μm or less, and is equal to or less than the thickness of the film portion 2. The thickness of the hard layer 10 may not be uniform, and may be partially different, as long as it is within the above thickness range. The hard layer 10 is not limited to one having a homogeneous structure, and may be made of, for example, a mesh-like film having openings (not shown). The material of the hard layer 10 is not limited, and may be, for example, a film of metal (e.g., aluminum, etc.), plastic (e.g., LDPE (low density polyethylene), PE (polyethylene), PP (polypropylene), PET (polyethylene terephthalate), PVC (polyvinyl chloride), or composite resins thereof), crosslinked (vulcanized) rubber, or thermoplastic elastomer. These plastics, crosslinked (vulcanized) rubbers, and thermoplastic elastomers may be made from raw materials derived from biomass.

[0022] According to the sound-proofing structure 1 of this embodiment, the vibration of the film portion 2 and the hard layer 10 is controlled by the action of a spring-mass resonator constituted by the spring portion 4a and the mass portion 4b of the weight portion 4. In particular, in a specific frequency range (for example, frequencies below 1000 Hz, which is the main frequency band of road noise in automobiles), the film vibration is significantly reduced, and as a result, the radiation sound from the film portion 2 and the hard layer 10 is reduced, and high sound insulation is achieved.

[0023] The section 5 of the sound insulation structure 1 of this embodiment has a membrane part 2 with an area of ​​1000 cm 2 It is preferable that 10 to 1000 sections are provided per unit area, and more preferably 50 to 500 sections are provided per unit area. If there are too few sections 5, the effect of dividing the entire sound insulation structure 1 into a plurality of sections 5 and having each section provide its own sound insulation effect is poor, and the sound insulation of the entire sound insulation structure 1 may be reduced. On the other hand, if there are too many sections 5, the weight of the entire sound insulation structure 1 may increase. The planar area of ​​each section 5 is 100 mm 2 More than 1000mm 2It is preferable that the length is less than 200 mm. 2 More than 800mm 2 It is more preferable that the height is 5 mm or less. If the area of ​​the planar shape of each section 5 is too small, it may be difficult to arrange the weight section 4 inside, and if the area is too large, the effect of the weight section 4 on the film section 2 may be poor, and the sound insulation may be reduced. The height of the entire sound insulation structure 1 in the direction perpendicular to the film section 2 is preferably 5 mm or more and 20 mm or less. If the height of the entire sound insulation structure 1 is too low, the weight section 4 may not have a sufficient height as a spring mass resonator, and if it is too high, the weight of the entire sound insulation structure 1 may increase. Each drawing shows each section 5 and the support wall section 3, etc., and the number and area of ​​the sections 5 and the height of the sound insulation structure 1 may not be shown strictly and accurately, or may not be unified in each drawing, but it is preferable that the number and area of ​​the sections 5 and the height of the sound insulation structure 1 are appropriately designed to be within the above-mentioned numerical ranges.

[0024] The film portion 2, the supporting wall portion 3, and the spring portion 4a of the sound insulation structure 1 of this embodiment are all made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa to 100 MPa at 23° C. and a loss tangent (tan δ) of 0.01 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, preferably a dynamic storage modulus (E') of 0.05 MPa to 50 MPa at 23° C. and a loss tangent (tan δ) of 0.05 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, respectively. The dynamic storage modulus (E') and the loss tangent (tan δ) are determined by creating a master curve based on 23° C. using a dynamic viscoelasticity tester. When the dynamic storage modulus (E') is 0.01 MPa or more at 23°C and frequencies of 1 Hz to 1000 Hz, the sound insulation performance in the target frequency band is good, and the shape retention of the film 2 and the supporting wall 3 is also good. When the dynamic storage modulus (E') is less than 100 MPa at 23°C and frequencies of 1 Hz to 1000 Hz, the vibration in the target frequency band for sound insulation is good, and the sound insulation structure 1 becomes rigid and easy to install. The film 2 and the supporting wall 3 may be made of the same material or different materials. It is preferable that the film 2 is also made of a flexible material, that is, a material that does not have energy elasticity but has rubber elasticity, a material that does not have rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity.

[0025] The film portion 2 is preferably a hard elastic film since the weight portion 4 is attached to it. The dynamic storage elastic modulus (E') of the film portion 2 is preferably 15 MPa or more, and the thickness (film thickness) is preferably 1 μm or more and 3000 μm or less, and more preferably 10 μm or more and 1000 μm or less. When the film portion 2 has a certain thickness or more, sufficient thickness can be secured, making it easy to handle. On the other hand, when the thickness of the film portion 2 is not too thick, an increase in the thickness and weight of the entire sound insulation structure 1 is prevented, and the entire sound insulation structure 1 does not become too hard, so that the installation is good. The material of the film portion 2 preferably has a durometer A hardness of 30 or more according to JIS K6253, and more preferably 70 or more. When the durometer A hardness of the film portion 2 is within the above range, deterioration of the vibration of the film portion 2 is prevented, and sound insulation in the frequency band to be sound-insulated is good. The stiffness (axial stiffness) k of the membrane 2 is expressed as k = E' × A / L from the dynamic storage modulus E', the cross-sectional area A of the membrane 2, and the thickness L of the membrane 2. When the area of ​​the membrane 2 to be evaluated for stiffness is 1000 cm 2 When the stiffness k is 10 4 N / mm or more 10 9 It is preferable that the resistance is less than 10 N / mm. 5 N / mm or more 10 8 It is more preferable that the surface area of ​​the membrane portion 2 is 1000 cm 2 When the stiffness is 10 4 When the surface area of ​​the film 2 is 1000 cm or more, the deterioration of the vibration of the film 2 can be suppressed, and the sound insulation performance in the frequency band to be insulated can be improved. 2 When the stiffness is 10 9 Since the elastic modulus is smaller than N / mm, the sound insulation structure 1 becomes flexible and easy to install. The bending stiffness K of the film 2 is expressed as K=E'×I from the dynamic storage elastic modulus E' and the second moment of area I, and the second moment of area I is expressed as I=b×h from the thickness h of the film 2 and the width b of the film 2. 3 / 12. When the area of ​​the membrane part 2 to be evaluated is 1000 cm 2 When the bending stiffness K is 1N / mm 2 Over 10 5 N / mm 2It is preferable that the resistance is less than 10 N / mm 2 5×10 or more 4 N / mm 2 It is more preferable that the area of ​​the membrane portion 2 is 1000 cm or less. 2 The bending stiffness K when 2 By satisfying the above, the film portion 2 has a good vibration and can suppress deterioration of the sound insulation performance in the frequency band to be sound-insulated. 2 When the bending stiffness K is 10 5 N / mm 2 When the thickness is as follows, the sound insulation structure 1 becomes flexible and the installation becomes easy. The cross-sectional shape of the film portion 2 is not particularly limited, and may be flat or may have irregularities.

[0026] Examples of materials for the membrane portion 2 include crosslinked (vulcanized) rubber, thermoplastic elastomer, and plastic. Examples of crosslinked (vulcanized) rubber include natural rubber (NR), isoprene rubber (IR), butadiene rubber (BR), styrene-butadiene rubber (SBR), chloroprene rubber (CR), butyl rubber (IIR), nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), ethylene-α-olefin-non-conjugated polyene copolymers such as ethylene-propylene rubber (EPM), ethylene-propylene-diene rubber (EPDM) and ethylene-butene-diene rubber (EBDM), chlorosulfonated polyethylene (CSM), chlorinated polyethylene (CM), acrylic rubber (ACM), ethylene-acrylic rubber (AEM), ethylene-vinyl acetate rubber (EVA), epichlorohydrin rubber (CO, ECO), polysulfide rubber (T), silicone rubber (Q) such as methylvinylsilicone rubber (VMQ) and fluorinated silicone rubber (FVMQ), urethane rubber (U), and fluororubber (FKM). These crosslinked (vulcanized) rubbers can be used alone or in combination of two or more kinds. Examples of the crosslinking (vulcanization) method include a method of crosslinking (vulcanization) by heating using an organic peroxide, a phenolic resin, an oxime compound, sulfur, a sulfur-based compound, or a polyamine compound as a crosslinking agent (vulcanizing agent), or a method of crosslinking by irradiating with an electron beam. The crosslinked (vulcanized) rubber may contain various known compounding agents (reinforcing agents such as carbon black and silica, fillers such as calcium carbonate, softeners such as paraffin oil and plasticizers, processing aids, antioxidants, light stabilizers, flame retardants, antifungal agents, acid acceptors, silane coupling agents, antistatic agents, ultraviolet absorbing agents, etc.) that are generally used as rubber compounding agents. These crosslinked (vulcanized) rubbers, crosslinking agents (vulcanizing agents), and compounding agents may be made from biomass raw materials.

[0027] Examples of the thermoplastic elastomer include olefin-based thermoplastic elastomers, styrene-based thermoplastic elastomers, polyester-based thermoplastic elastomers, polyvinyl chloride-based thermoplastic elastomers, and ethylene-vinyl acetate-based thermoplastic elastomers. Examples of the plastic include polyethylene, polypropylene, polystyrene, polyethylene terephthalate, polyvinyl chloride, and composite resins containing these. These thermoplastic elastomers and plastics may be made from biomass raw materials.

[0028] Specifically, the material of the film portion 2 is preferably ethylene-propylene-diene rubber, a thermoplastic olefin-based elastomer, a thermoplastic styrene-based elastomer, polyethylene, polypropylene, polyethylene terephthalate, thermoplastic polyurethane, or the like.

[0029] The supporting wall 3 is preferably made of a soft, flexible material within a range capable of supporting the film 2. The plate thickness of the supporting wall 3 is preferably 0.5 mm or more and 5.0 mm or less, and more preferably 1.0 mm or more and 3.0 mm or less. When the plate thickness of the supporting wall 3 is 0.5 mm or more, the shape retention of the sound insulation structure 1 is good. When the plate thickness of the supporting wall 3 is 5.0 mm or less, the vibration of the film 2 is good, the sound insulation of the frequency band to be sound-insulated is good, and the increase in the weight of the entire sound insulation structure 1 can be suppressed. The height of the supporting wall 3 extending in a direction perpendicular to the film 2 is preferably 5 mm or more and 20 mm or less, and more preferably 10 mm or more and 20 mm or less. The supporting wall 3 may have a different height in parts. When the height of the supporting wall 3 is different in parts, the higher part may be 10 mm or more and 20 mm or less, more preferably 12 mm or more and 20 mm or less, and even more preferably 14 mm or more and 20 mm or less. The support wall 3 is not too low in height, so that the weight 4 can have a sufficient height as a spring mass resonator. The support wall 3 is not too high in height, so that the overall weight can be reduced. The material of the support wall 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. The support wall 3 has a durometer A hardness of 1 or more, so that the shape retention of the sound insulation structure 1 can be maintained. The support wall 3 has a durometer A hardness of 90 or less, so that the vibration from the support wall 3 is prevented from being transmitted to the membrane 2, which would deteriorate the sound insulation performance, and the sound insulation structure 1 becomes flexible and easy to install. The stiffness k of the support wall 3 is expressed as k=E'×A / L, where E' is the dynamic storage elastic modulus, A is the cross-sectional area of ​​the support wall 3, and L is the height of the support wall 3. When the area of ​​the support wall 3 to be evaluated for stiffness is 1000 cm 2 When the stiffness k is 10N / mm or more, 6 It is preferable that the resistance is less than 10 N / mm. 2 N / mm or more 10 5 It is more preferable that the surface area of ​​the support wall 3 is 1000 cm or less. 2When the area of ​​the support wall 3 is 1000 cm, the stiffness k is 10 N / mm or more, so that the shape retention of the sound insulation structure 1 can be maintained. 2 When the stiffness k is 10 6 By setting the resistance to N / mm or less, vibrations from the supporting wall portion 3 are prevented from being transmitted to the membrane portion 2, which would deteriorate the sound insulation performance, and the sound insulation structure 1 becomes rigid, making it easier to install.

[0030] Examples of the material of the support wall 3 include crosslinked (vulcanized) rubber, thermoplastic elastomer, and resin foam. The crosslinked (vulcanized) rubber and thermoplastic elastomer may be the same as the materials listed as the materials of the membrane 2. The resin foam may have a closed cell structure or an open cell structure, and examples of the resin foam include polyurethane foam, polystyrene foam, polyethylene foam, and ethylene-vinyl acetate rubber (EVA) foam. Specifically, the material of the support wall 3 is preferably ethylene-propylene-diene rubber, urethane rubber, silicone rubber, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, thermoplastic polyurethane, and polyurethane foam. These resin foams may be made of biomass raw materials.

[0031] The material of the spring portion 4a of the weight portion 4 is a flexible material such as crosslinked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. The crosslinked (vulcanized) rubber, thermoplastic elastomer, and resin foam may be the same as the materials given as the materials of the support wall portion 3. Specifically, the material of the spring portion 4a of the weight portion 4 is preferably ethylene-propylene-diene rubber, urethane rubber, silicone rubber, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, thermoplastic polyurethane, polyurethane foam, etc.

[0032] The material of the mass portion 4b is not particularly limited, but it is made of resin, metal, or the like, and the mass portion 4b has a larger mass than the spring portion 4a, for example, a mass of 0.1 g or more and 2.0 g or less. The mass portion 4b preferably has a mass at least twice the mass of the spring portion 4a. If the weight of the mass portion 4b is less than twice the mass of the spring portion 4a, the weight portion 4 cannot resonate sufficiently in the frequency range to be sound-insulated, and sound insulation may be deteriorated. When the material of the mass portion 4b is resin, the resin may be made of a biomass material.

[0033] The spring constant (rigidity) of the spring portion 4a is determined based on the mass of the mass portion 4b so that the resonant frequency coincides with the frequency to be mainly sound-insulated. As an example, when the mass portion 4b has a mass of 1.0 g and the frequency to be mainly sound-insulated is 1000 Hz or less, the spring constant of the spring portion 4a is 1 N / mm or more and 50 N / mm or less.

[0034] As described above, the hard layer 10 is not limited to one having a homogeneous structure, but is made of a film harder than the film portion 2. The material of the hard layer 10 is not limited, but may be metal (e.g., aluminum, etc.), plastic, crosslinked (vulcanized) rubber, thermoplastic elastomer, or composite resin containing them. The plastic, crosslinked (vulcanized) rubber, and thermoplastic elastomer may be the same as the materials listed as the materials of the film portion 2. The hard layer 10 is preferably a resin film. The thickness of the hard layer 10 is thinner than that of the film portion 2, and is preferably 1 μm or more and 3000 μm or less, and more preferably 10 μm or more and 1000 μm or less. If the thickness of the hard layer 10 is less than 1 μm, it is too thin and difficult to handle. If the thickness of the hard layer 10 is 3000 μm or more, it is heavy and the entire sound insulation structure 1 becomes rigid, which may deteriorate the installation. The hard layer 10 has a dynamic storage modulus (E') of 1 MPa or more at 23°C and a frequency of 1 Hz to 1000 Hz. 5 MPa or less, and preferably 10 MPa or more and 10 4If the dynamic storage modulus (E') of the hard layer 10 at 23°C and a frequency of 1 Hz to 1000 Hz is less than 1 MPa, the hard layer 10 is too soft and difficult to handle. 5 If it is greater than MPa, the entire sound-insulating structure 1 may become rigid, which may reduce ease of installation, and the frequency band in which a large sound-insulating effect is obtained may shift to the higher frequency side, which may reduce the sound-insulating properties in the frequency band that is the main target for sound insulation (for example, the frequency band below 1 kHz).

[0035] As described above, since the hard layer 10 is laminated on the film portion 2, even if the film portion 2 itself is thin and soft, it can support the supporting wall portion 3 and the weight portion 4, and the spring mass resonator formed by the spring portion 4a and the mass portion 4b of the weight portion 4 works well, and excellent sound insulation can be obtained. Furthermore, even if the supporting wall portion 3 is also thin and soft like the film portion 2, excellent sound insulation can be obtained by the action of the spring mass resonator. Since the supporting wall portion 3 is soft, it is easy to install it on various members (for example, automobile panels having unevenness or curved surfaces). Thus, in this embodiment, the film portion 2, the supporting wall portion 3, the weight portion 4, and the hard film 10 are all relatively light, and the dimensions in the direction perpendicular to the film portion 2 are relatively small. Thus, the sound insulation structure 1 of this embodiment is light and thin, but as described above, high sound insulation can be obtained in a specific frequency range (for example, 1000 Hz or less). Furthermore, the support wall portion 3 made of a flexible material can be easily and stably installed on a flat placement surface as well as a curved or uneven placement surface without being fixed thereto by adhesive or the like.

[0036] FIG. 3(A) is a perspective view of a sound insulation structure 1 of a modification of the first embodiment of the present invention, and FIG. 3(B) is a cross-sectional view taken along line AA in FIG. 3(A) and inverted upside down. FIG. 4(A) is a cross-sectional view of the sound insulation structure 1 of another modification, and FIG. 4(B) is a perspective view of the weight portion 4 of the sound insulation structure 1. FIG. 5(A) is a cross-sectional view of the sound insulation structure 1 of yet another modification, and FIG. 5(B) is a perspective view of the weight portion 4 of the sound insulation structure 1. In these modifications, the spring portion 4a and the mass portion 4b of the weight portion 4 have different shapes and different dimensions. In the modifications shown in FIGS. 3(A) and 3(B), the spring portion 4a is a small-diameter cylindrical portion, and the mass portion 4b is a large-diameter cylindrical portion. In the modifications shown in FIGS. 4(A) and 4(B), the spring portion 4a is an elongated cylindrical portion, the mass portion 4b is a spherical portion, and the diameter of the cross-sectional shape of the cylindrical spring portion 4a is smaller than the diameter of the spherical mass portion 4b. In the modified example shown in Figs. 5(A) and 5(B), the spring portion 4a is in a truncated cone shape, the mass portion 4b is in a cylindrical shape, and the diameter of the smallest part of the truncated cone spring portion 4a is substantially equal to the diameter of the cylindrical mass portion 4b. In the modified example shown in Figs. 3(A) to 4(B), the mass portion 4b has a larger volume than the spring portion 4a. Therefore, even if the spring portion 4a and the mass portion 4b are made of the same material, the mass portion 4b has a larger mass than the spring portion 4a, and a spring-mass resonator can be configured. However, in this modified example, the spring portion 4a and the mass portion 4b may be made of different materials, and the mass portion 4b may have a larger mass than the spring portion. On the other hand, in the modified example shown in Figs. 5(A) and 5(B), the spring portion 4a has a larger volume than the mass portion 4b. In this case, the mass portion 4b is made of a material having a higher density than the spring portion 4a, and the mass portion 4b has a larger mass than the spring portion, and a spring-mass resonator can be configured. As in the modified example shown in Figures 5(A) and 5(B), when the spring portion 4a is a truncated cone tapered in the direction away from the membrane portion 2, the membrane portion 2 and the spring portion 4a are easily releasable from a mold when they are molded integrally.

[0037] In this embodiment, the spring portion 4a and the mass portion 4b of the weight portion 4 are made different in either material or volume or both, so that the mass portion 4b has a larger mass than the spring portion 4a to configure a spring mass resonator and obtain a sufficient sound insulation effect. That is, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b are determined so that a spring mass resonator that can provide a sufficient sound insulation effect can be configured. As long as the mass of the mass portion 4b can be made larger than the spring portion 4a to the extent that a spring mass resonator that can provide a sufficient sound insulation effect can be configured in this way, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b can be freely selected. However, the spring portion 4a needs to be made of a flexible material in order to function as a spring.

[0038] [Second embodiment] FIG. 6(A) is a perspective view of a sound insulation structure 6 according to a second embodiment of the present invention, and FIG. 6(B) is a cross-sectional view taken along line AA in FIG. 6(A) and turned upside down. The sound insulation structure 6 has a weight 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 7 functions as a mass portion, and the film portion 2 and the hard layer 10 function as a spring portion. As an example, the mass of the weight 7 is about 0.1 g to 2.0 g. The material of the weight 7 is not limited, and it is formed from, for example, a synthetic resin or metal. The other configurations are the same as those of the first embodiment described above, so that the description will be omitted. In the sound insulation structure 6 of this embodiment, the membrane vibration is also controlled by the action of the spring-mass resonator formed by the weight 7, the film portion 2, and the hard layer 10, and the membrane vibration is significantly reduced in a specific frequency range (for example, 1000 Hz or less), and high sound insulation is exhibited. In addition, the air in the space surrounded by the membrane portion 2 and the support wall portion 3, together with the membrane portion 2 and the hard layer 10, may function as a part of the spring of the spring mass resonator (air spring).

[0039] In both the film part 2 and the supporting wall part 3 of this embodiment, the dynamic storage modulus (E') at 23°C and at a frequency of 1 Hz to 1000 Hz is preferably 0.01 MPa or more and 100 MPa or less, and the loss tangent (tan δ) at 23°C and at a frequency of 1 Hz to 1000 Hz is preferably 0.01 or more and 0.50 or less. Furthermore, in both the film part 2 and the supporting wall part 3 of this embodiment, the dynamic storage modulus (E') at 23°C and at a frequency of 1 Hz to 1000 Hz is more preferably 0.05 MPa or more and 50 MPa or less, and the loss tangent (tan δ) at 23°C and at a frequency of 1 Hz to 1000 Hz is more preferably 0.05 or more and 0.50 or less. In this embodiment, the hard layer 10 is thinner than the film part 2, having a thickness of 1 μm or more and 3000 μm or less, and is harder than the film part 2. In addition, the hard layer 10 is more preferably harder than the film part 2, having a dynamic storage modulus (E') at 23°C and at a frequency of 1 Hz to 1000 Hz. 5 It is preferable that the compressive strength is not more than 100 MPa.

[0040] The support wall 3 of this embodiment is made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane 2 of this embodiment is made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0041] Fig. 7(A) is a cross-sectional view of a sound insulation structure 6 according to a modification of the second embodiment of the present invention, and Fig. 7(B) is a perspective view of the weight 7 of the sound insulation structure 6. In this modification, the weight 7 has a truncated cone shape that tapers away from the film 2. With this configuration, the film 2 and the weight 7 are easily releasable from a mold when they are integrally molded. In this embodiment, the shape of the weight 7 can be determined arbitrarily and is not particularly limited.

[0042] In any of the first and second embodiments, the film portion 2 and the supporting wall portion 3 can be formed by integral molding or two-color molding using the above-mentioned materials by injection molding, compression molding, press molding, extrusion molding, transfer molding, casting, etc. Furthermore, the weight portions 4, 7 and the hard layer 10 can also be formed by integral molding, two-color molding, insert molding, etc. using the above-mentioned materials together with the film portion 2 and the supporting wall portion 3 in some cases. However, the film portion 2, the supporting wall portion 3, the weight portions 4, 7 and the hard layer 10 may be formed separately from each other, and then joined together by adhesion or heat fusion to assemble the sound-insulating structures 1, 6.

[0043] In the configuration of the sound insulation structures 1 and 6 described above, as shown in Figs. 8(A) and 8(B), the support wall 3 includes a plurality of first wall portions 3a extending in a first direction D1 parallel to the film portion 2 and a plurality of second wall portions 3b extending in a second direction D2 perpendicular to the first direction D1, and the planar shape of each section 5 is a square. In other words, the support wall portion 3 is a square tube having a square cross-sectional shape that defines each section 5, and a large number of square tube-shaped support wall portions 3 are arranged side by side, and the support wall portions 3 of adjacent sections 5 are integrated. However, the configuration is not limited to this. For example, as shown in Figs. 9(A) and 9(B), the planar shape of each section 5 may be a triangle, and the support wall portion 3 may be a square tube having a triangular cross-sectional shape that defines each section 5. As shown in Figs. 10(A) and 10(B), the planar shape of each section 5 may be pentagonal, and the support wall 3 may be a square tube having a pentagonal cross-sectional shape that defines each section 5. As shown in Figs. 11(A) and 11(B), the planar shape of each section 5 may be hexagonal, and the support wall 3 may be a square tube having a hexagonal cross-sectional shape that defines each section 5, forming a so-called honeycomb structure. Furthermore, as shown in Figs. 12(A) and 12(B), the planar shape of each section 5 may be circular, and the support wall 3 may be a cylinder having a circular cross-sectional shape that defines each section 5. In the case of the configuration shown in Figs. 10(A), 10(B), 12(A), and 12(B), gaps are generated between the sections 5, so it is preferable to determine the shape and dimensions of the support wall 3 so as to reduce the gaps. In the configurations shown in Figures 8(A), 8(B), 9(A), 9(B), 11(A), and 11(B), no gaps are generated 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 oval, or may have an irregular shape. The support wall portion 3 is formed to have a shape and dimensions that match the planar shape of each compartment 5.

[0044] The sound insulation structures 1, 6 of the present invention are very thin and lightweight, and can be easily placed on a curved or uneven surface, so they may be placed on the panel of a vehicle, particularly an automobile, for use. The panel of an automobile or the like is basically a plate with no air permeability, and examples thereof include a metal plate (iron plate, steel plate, aluminum plate) and a resin plate. When the panel on which the sound insulation structure 1 is placed is a metal plate, its thickness is preferably in the range of 0.5 mm to 2.0 mm, and when it is a resin plate, its thickness is preferably in the range of 0.5 mm to 20 mm. When the sound insulation structures 1, 6 are placed on the panel of an automobile, it is preferable that the end face of the support wall portion 3 of the sound insulation structures 1, 6 opposite to the side attached to the film portion 2 is placed on the panel. In this case, the support wall portion 3 and the panel may or may not be bonded to each other, but it is preferable that the support wall portion 3 is placed on the panel without being bonded to the panel.

[0045] The sound insulation structure 1,6 of the present invention may be used alone or in combination with other members (not shown). When the sound insulation structure 1,6 of the present invention is used in combination with other members, it may be laminated or joined to the other members. When laminated or joined to other members, the sound insulation structure 1,6 may be placed so as to be in contact with the portion (e.g., an automobile panel) on which the sound insulation structure 1,6 is placed, or the other members may be placed so as to be in contact with the portion. The other members used in combination with the sound insulation structure 1,6 may be made of various materials.

[0046] Examples of locations in an automobile where the sound insulation structures 1, 6 of the present invention are installed include, in the engine compartment, engine head covers, engine body covers, hood insulators, front-dash insulators, air box walls, air intake cleaners, dust side ducts, under covers, etc.; in the cabin, examples include dash insulators, dash panels, floor carpets (floor silencers), spacers, door trims, the inside of door trims, instrument panels, instrument center boxes, instrument upper boxes, air conditioner housings, roof trims, the inside of roof trims, sun visors, air conditioning ducts for rear seats, cooling ducts of battery cooling systems in battery-equipped vehicles, cooling fans, center console trims, the inside of the console, parcel trims, parcel panels, seat headrests, front seat backs, rear seat backs, etc.; and in the trunk, examples include trunk side trims, the inside of trims, and drafter covers. In addition, the sound-insulating structures 1, 6 of the present invention can be installed within the frame of an automobile or between panels, and can also be installed in under-covers under the floor located outside the vehicle, fender protectors, back doors, wheel covers, aerodynamic covers for suspensions, and the like.

[0047] Specific examples and comparative examples of the sound insulation structure of the present invention will be described below. [Example 1] The sound insulation structure 1 of the first embodiment of the present invention has the same structure as that of the first embodiment shown in Figs. 1 and 2. The film portion 2 is made of urethane rubber having a durometer A hardness of 30 according to JIS K6253 and a film thickness of 1.0 mm. The film portion 2 has a dynamic storage modulus (E') of 1.08 MPa at 23°C and a frequency of 1 Hz, and a loss tangent (tan δ) of 0.100 at 23°C and a frequency of 1 Hz. The dynamic storage modulus (E') of 1.28 MPa at 23°C and a frequency of 10 Hz and a loss tangent (tan δ) of 0.155, the dynamic storage modulus (E') of 1.64 MPa at 23°C and a frequency of 100 Hz and a loss tangent (tan δ) of 0.209, and the dynamic storage modulus (E') of 2.58 MPa at 23°C and a frequency of 1000 Hz and a loss tangent (tan δ) of 0.275. The planar shape of the film portion 2 has an area of ​​1000 cm. 2 If the square is 28.4N / mm 2 and the axial stiffness k is 1.08×10 5 N / mm. The supporting wall 3 in this embodiment is made of urethane rubber having the same durometer A hardness of 30 as the film portion 2 and a film thickness of 1.2 mm. The height of the supporting wall 3 (the dimension in the direction perpendicular to the film portion 2) is 10 mm. The axial stiffness k of the supporting wall 3 is 1.01×10 3 N / mm. The compartments 5 defined by the multiple support walls 3 (first wall 3a and second wall 3b) are square, measuring 25 mm x 25 mm, and there are 49 compartments 5 in the 200 mm x 200 mm square area (evaluation surface) of the membrane 2. However, the drawing shows only a portion of this area. The weight 4 is cylindrical, with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane 2) of 6 mm.

[0048] Of the weight portion 4, the spring portion 4a, which is the portion attached to the membrane portion 2, is 3 mm in height and is made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tan δ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the spring portion 4a in this embodiment has a dynamic storage modulus (E') of 0.60 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 1 Hz, a dynamic storage modulus (E') of 0.74 MPa and a loss tangent (tan δ) of 0.24 at 23° C. and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.97 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 100 Hz, and a dynamic storage modulus (E') of 1.31 MPa and a loss tangent (tan δ) of 0.16 at 23° C. and a frequency of 1000 Hz, and is made of silicone rubber with a durometer A hardness of 10 according to JIS K6253. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side attached to the membrane portion 2, also has a height of 3 mm and is made of stainless steel (SUS304) having rigidity. Mass 4 has a mass of approximately 0.8 g, and has a resonance that shows a peak frequency at 600 Hz to 650 Hz in the direction perpendicular to the surface on which mass 4 is placed.

[0049] In this embodiment, the hard layer 10 is an LDPE film having a thickness of 0.05 mm. The height of the entire sound insulation structure 1 is 11.05 mm, and the surface density of the entire sound insulation structure 1 including the membrane portion 2, the support wall portion 3, the weight portion 4, and the hard layer 10 in one section 5 is 2.40 kg / m 2 The surface density is a value calculated from the weight and area of ​​the sample.

[0050] As shown in Fig. 13, the end face of the support wall 3 of the sound insulation structure 1 opposite to the side attached to the film 2 was placed on a 0.8 mm thick iron plate 8, and the sound insulation was measured with the surface of the iron plate 8 opposite to the side on which the sound insulation structure 1 was placed as the incident sound side. Specifically, in accordance with the intensity method shown in JIS A1441-1, a test facility room with a reverberation room as the sound source room and a semi-anechoic room as the sound receiving room was used, and the sound transmission loss (transmission loss) [dB] was obtained for the 1 / 3 octave band center frequency [Hz] by 1 / 3 octave band analysis. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss was obtained and is shown in Table 1 and Figs. 14(A) to 14(E). The larger the sound transmission loss, the higher the sound insulation. In the 1 / 3 octave band center frequencies [Hz] shown in FIGS. 14(A) to 14(E), 1 kHz is 1000 Hz, and the prefix "k" means 1000.

[0051] [Table 1]

[0052] [Example 2] A sound insulation structure 1 of Example 2 of the present invention has the same structure as that of the first embodiment shown in Figures 1 and 2. The weight portion 4 and hard layer 10 of this example are the same as the weight portion 4 and hard layer 10 of Example 1. The film portion 2 and supporting wall portion 3 of this example are made of urethane rubber having a durometer A hardness of 70 according to JIS K6253. The film part 2 and the supporting wall part 3 have a dynamic storage modulus (E') of 6.88 MPa at 23°C and a frequency of 1 Hz, a loss tangent (tan δ) of 0.077 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 7.87 MPa at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 9.66 MPa at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 12.6 MPa at 23°C and a frequency of 1000 Hz. The dimensions of the film part 2 and the supporting wall part 3 are the same as those of the film part 2 and the supporting wall part 3 in Example 1. The surface density of this configuration is 2.50 kg / m 2The end face of the supporting wall portion 3 of this sound insulation structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Table 1 and FIG.

[0053] [Example 3] A sound insulation structure 1 of Example 3 of the present invention has the same structure as that of the first embodiment shown in Figures 1 and 2. The weight portion 4 and hard layer 10 of this example are the same as the weight portion 4 and hard layer 10 of Example 1. The film portion 2 and supporting wall portion 3 of this example are made of urethane rubber having a durometer A hardness of 90 according to JIS K6253. The film part 2 and the supporting wall part 3 have a dynamic storage modulus (E') of 31.3 MPa at 23°C and a frequency of 1 Hz, a loss tangent (tan δ) of 0.115 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 37.3 MPa at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 44.2 MPa at 23°C and a frequency of 100 Hz, and a dynamic storage modulus (E') of 57.8 MPa at 23°C and a frequency of 1000 Hz. The dimensions of the film part 2 and the supporting wall part 3 are the same as those of the film part 2 and the supporting wall part 3 in Example 1. The surface density of this configuration is 2.57 kg / m 2 The end face of the supporting wall portion 3 of this sound insulation structure 1 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Table 1 and FIG.

[0054] [Example 4] The sound insulation structure 1 of the fourth embodiment of the present invention has the same structure as the modified example of the first embodiment shown in FIG. 3. The film portion 2 and the supporting wall portion 3 of this embodiment are the same as the film portion 2 and the supporting wall portion 3 of the first embodiment. The weight portion 4 of this embodiment 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 portion of the weight portion 4 attached to the film portion 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the film portion 2) of 3 mm, and is made of the same material (silicone rubber with a durometer A hardness of 10 according to JIS K6253-3) as the spring portion 4a of the weight portion 4 of the first embodiment. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side attached to the film portion 2, is cylindrical with a diameter of 13 mm and a height of 5 mm, and is made of EPDM with a durometer A hardness of 65 according to JIS K6253-3. The weight portion 4 has a mass of about 1.0 g. The hard layer 10 in this embodiment is a PE film having a thickness of 0.05 mm. The surface density of this structure is 2.60 kg / m 2 As shown in Fig. 15, the end face of the supporting wall 3 of this sound-insulating structure 1 opposite to the side attached to the film 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Table 1 and Fig. 14(C).

[0055] [Example 5] The sound insulation structure 1 of Example 5 of the present invention has the same structure as the modified example of the first embodiment shown in Fig. 3. The film part 2 and the supporting wall part 3 of this example are made of a styrene-based thermoplastic elastomer (TPS) having a durometer A hardness of 50 according to JIS K6253. The film part 2 and the supporting wall part 3 have a dynamic storage modulus (E') of 7.81 MPa at 23°C and a frequency of 1 Hz, a loss tangent (tan δ) of 0.065 at 23°C and a frequency of 1 Hz, a dynamic storage modulus (E') of 8.62 MPa at 23°C and a loss tangent (tan δ) of 0.079 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 9.19 MPa at 23°C and a loss tangent (tan δ) of 0.113 at 23°C and a frequency of 1000 Hz, and a dynamic storage modulus (E') of 10.3 MPa at 23°C and a loss tangent (tan δ) of 0.084 at 23°C and a frequency of 1000 Hz. The dimensions of the film portion 2 and the supporting wall portion 3 are the same as those of the film portion 2 and the supporting wall portion 3 in Example 1. The weight portion 4 in 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 portion of the weight portion 4 attached to the film portion 2, is cylindrical with a diameter of 6 mm and a height (dimension in the direction perpendicular to the film portion 2) of 3 mm, and the mass portion 4b, which is the portion opposite to the side attached to the film portion 2, is cylindrical with a diameter of 9 mm and a height of 6 mm. Both the spring portion 4a and the mass portion 4b are made of TPS with a durometer A hardness of 5 according to JIS K6253-3. The spring portion 4a and the mass portion 4b have a dynamic storage modulus (E') of 0.21 MPa at 23°C and a frequency of 1 Hz, a loss tangent (tan δ) of 0.038 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 0.031 at 23°C and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.28 MPa and a loss tangent (tan δ) of 0.051 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. The hard layer 10 of this embodiment is a PE film having a thickness of 0.05 mm. The surface density of this structure is 2.39 kg / m 2As shown in Fig. 16, the end face of the supporting wall 3 of this sound-insulating structure 1 opposite to the side attached to the film 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Table 1 and Fig. 14(C).

[0056] [Example 6] The sound insulation structure 1 of Example 6 of the present invention has the same structure as that of the first embodiment shown in Figures 1 and 2. The film portion 2, the supporting wall portion 3, and the weight portion 4 of this example are the same as those of Example 1. The hard layer 10 of this example is a PE film with a thickness of 1 mm. The surface density of this structure is 3.28 kg / m 2 The end face of the supporting wall 3 of this sound insulation structure 1 opposite to the side attached to the film 2 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation performance, which is shown in Table 1 and FIG.

[0057] [Comparative Example 1] As Comparative Example 1, a member having the same mass as the sound insulation structure 1 of Example 1 is placed on a 0.8 mm thick iron plate 8. The theoretical sound insulation value calculated based on the mass law was obtained, and the relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Table 2 and Figure 14(A). The surface density of this structure is 2.40 kg / m 2 It is.

[0058] [Table 2]

[0059] [Comparative Example 2] As Comparative Example 2, as shown in Fig. 17, sound insulation was measured in a state where nothing was 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 Figs. 14(A) to 14(E). This shows a state where no sound insulation structure is provided. The surface density of the iron plate 8 is 6.02 kg / m 2 It is.

[0060] [Comparative Example 3] As Comparative Example 3, as shown in Figures 18(A) and 18(B), a structure 12 consisting only of a film portion 2 and a supporting wall portion 3 was placed on a 0.8 mm thick iron plate 8 to measure sound insulation, and the relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in Figure 14(E). The film portion 2 and supporting wall portion 3 of this Comparative Example are the same as the film portion 2 and supporting wall portion 3 of Example 1, but the weight portion 4 and hard layer 10 are not present. The surface density of this structure 12 is 1.70 kg / m 2 It is.

[0061] [Comparative Example 4] In Comparative Example 4, as shown in FIG. 19, a hard layer 10 was placed on a 0.8 mm thick iron plate 8 with a gap of 10 mm (air layer 11). The hard layer 10 in this Comparative Example was the same as the hard layer 10 in Examples 4 and 5. The sound insulation of this structure was measured, and the relationship between the 1 / 3 octave band center frequency and the sound transmission loss is shown in FIG. 14(E). The surface density of this structure was 0.15 kg / m 2 It is.

[0062] [Comparative Example 5] As Comparative Example 5, a structure 13 consisting of a film portion 2, a supporting wall portion 3, and a weight portion 4 was manufactured. The film portion 2, the supporting wall portion 3, and the weight portion 4 of this Comparative Example are the same as the film portion 2, the supporting wall portion 3, and the weight portion 4 of Example 1. The structure 13 of this Comparative Example does not have a hard layer 10. As shown in FIG. 20, the end face of the supporting wall portion 3 of this structure 13 opposite to the side attached to the film portion 2 was placed on a 0.8 mm thick iron plate 8 to determine the sound insulation, which is shown in Table 2 and FIG. 14(A). The surface density of this structure 13 was 2.25 kg / m 2 It is.

[0063] [Comparative Example 6] As Comparative Example 6, a structure 14 consisting of a film portion 2, a supporting wall portion 3, and a hard layer 10 was manufactured. The film portion 2 and the supporting wall portion 3 of this comparative example are the same as the film portion 2 and the supporting wall portion 3 of Example 1. The film portion 2 and the supporting wall portion 3 of this comparative example are the same as the film portion 2 and the supporting wall portion 3 of Example 1. The hard layer 10 of this comparative example is the same as the hard layer 10 of Examples 4 to 5. The structure 14 of this comparative example does not have a weight portion 4. As shown in Figures 21(A) and 21(B), the end face of the supporting wall portion 3 of this structure 14 opposite to the side attached to the film portion 2 was placed on an iron plate 8 with a thickness of 0.8 mm to determine the sound insulation, which is shown in Table 2 and Figure 14(E). The surface density of this structure 14 was 2.11 kg / m 2 It is.

[0064] [Comparative Example 7] As Comparative Example 7, a structure 15 consisting of a support wall portion 3, a weight portion 4, and a hard layer 10 was manufactured. The weight portion 4 of this comparative example is the same as the weight portion 4 of Example 1. The hard layer 10 of this comparative example is the same as the hard layer 10 of Examples 4 to 5. The support wall portion 3 of this comparative example is made of an elastic body having 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, and 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. More specifically, the supporting wall 3 of this comparative example has 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, a dynamic storage modulus (E') of 2.33 MPa and a loss tangent (tan δ) of 0.12 at 23°C and a frequency of 1000 Hz, a durometer A hardness of 30 according to JIS K6253-3, a plate thickness of 1.6 mm, and a height of 10 mm in a direction perpendicular to the film 2. The structure 15 of this comparative example does not have a film 2, and the end face of the supporting wall 3 is attached to the hard layer 10. As shown in Fig. 22, the end face of the supporting wall 3 of this structure 15 opposite to the side attached to the hard layer 10 was placed on a 0.8 mm thick iron plate 8 to measure the sound insulation, which is shown in Table 2 and Fig. 14(D). The surface density of this structure 15 was 1.98 kg / m 2 It is.

[0065] [result] The results of comparing the above-mentioned Examples 1 to 6 of the present invention with Comparative Examples 1 to 7 will be described. Referring to Figs. 14(A) to 14(E), it can be seen that the sound insulation effect is improved by the sound insulation structure 1 of the present invention. In particular, the sound insulation structure 1 of Example 1 provides a significantly greater sound insulation effect than the theoretical value based on the mass law (Comparative Example 1), and it can be seen that the effect of the present invention is particularly large in the frequency band of 1 kHz or less. The structure of the film part 2 and the supporting wall part 3 of the sound insulation structure 1 creates an air layer between the iron plate 8, resulting in a hollow double wall effect, which increases the sound insulation on the high frequency side, thereby providing high sound insulation for the frequency band of 1 kHz or more. This effect is also shown in Comparative Examples 3 and 5 shown in Figs. 14(A) and 14(E). In addition, according to Example 1 of the present invention, high sound insulation can be obtained not only for the frequency band of 1 kHz or more, but also for the frequency band of 1 kHz or less. This effect is mainly due to the action of the spring mass resonator formed by the weight part 4 and the action of the hard layer 10. Also, referring to FIG. 14(C), it is understood that good sound insulation can be obtained from Example 4 even if the mass part 4b of the weight part 4 is made of a resin material, and it is understood that good sound insulation can be obtained from Example 5 even if the film part 2, the supporting wall part 3, and the weight part 4 are made of a thermoplastic material, and the spring part 4a and the mass part 4b of the weight part 4 are made of the same material. Referring to FIG. 14(A), it is understood that a good sound insulation effect can be obtained by providing the sound insulation structure 1 of the present invention, compared with Comparative Example 2 which does not have a sound insulation structure. Also, referring to FIG. 14(E), it is understood that good sound insulation cannot be obtained from the structure 12 of Comparative Example 3 which does not have the weight part 4 and the hard layer 10, the structure of Comparative Example 4 which has only the hard layer 10 and the air layer 11, and the structure 14 of Comparative Example 6 which does not have the weight part 4. Furthermore, referring to FIG. 14(A), it is understood that the structure 13 of Comparative Example 5 which does not have the hard layer 10 also does not have very good sound insulation, especially in the frequency band of 1 kHz or less. 14(D), it can be seen that good sound insulation properties are not obtained even with the structure 15 of Comparative Example 7, which has the hard layer 10 but does not have the film portion 2. In contrast, it can be seen that a better sound insulation effect is obtained with the sound insulation structure 1 of the present invention, which has the hard layer 10 in addition to the film portion 2, supporting wall portion 3, and weight portion 4.It is also clear that by providing a thin hard layer 10 as in Example 1, good sound insulation can be obtained even if the film portion 2 and the supporting wall portion 3 are of a flexible construction.

[0066] FIG. 14(B) shows the sound insulation of the sound insulation structure 1 of Example 1 and the sound insulation of the sound insulation structures 1 of Examples 2 and 3 in which the film portion 2 and the supporting wall portion 3 are harder than those of Example 1. Referring to FIG. 14(B), it can be seen that the frequency band in which the sound insulation effect is large is shifted to the high frequency side (for example, 800 Hz to 1 kHz) by forming the film portion 2 and the supporting wall portion 3 with a harder material. In this way, by adjusting the hardness of the film portion 2 and the supporting wall portion 3, it is possible to adjust the wave number band in which the sound is mainly insulated. However, if the film portion 2 and the supporting wall portion 3 are excessively hard, the frequency band in which the sound insulation effect is large is shifted further to the high frequency side, and the sound insulation of the frequency band (just under 1 kHz) that should mainly be insulated may rather deteriorate, and the entire sound insulation structure 1 may become hard and the installation may become difficult. Therefore, it is preferable to appropriately adjust the hardness of the film portion 2 and the supporting wall portion 3.

[0067] FIG. 14(D) shows the sound insulation of the sound insulation structure 1 of Example 1 and the sound insulation of the sound insulation structure 1 of Example 6, in which the hard layer 10 is thicker than that of Example 1. Referring to FIG. 14(D), it can be seen that the frequency band in which the sound insulation effect is large shifts to the high frequency side by making the hard layer 10 thicker. In this way, it is possible to adjust the wave number band that is mainly sound-insulated by adjusting the material and thickness of the hard layer 10. However, if the hard layer 10 is excessively thick, the frequency band in which the sound insulation effect is large shifts further to the high frequency side, and the sound insulation of the frequency band that should mainly be sound-insulated (just under 1 kHz) may rather deteriorate, and the entire sound insulation structure 1 may become hard, which may cause poor installation and weight, and may increase in weight. Therefore, it is preferable to appropriately adjust the material and thickness of the hard layer 10.

[0068] [1] A device having an elastic membrane portion, an elastic support wall portion standing on the membrane portion, a weight portion standing on the membrane portion, and a hard layer laminated on a surface of the membrane portion opposite to a surface on which the support wall portion and the weight portion are provided, 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; Each of the weight portions constitutes a spring mass resonator having a spring portion having elasticity and a mass portion having a mass larger than that of the spring portion, A sound-insulating structure, characterized in that the hard layer has a thickness of 1 μm or more and 3000 μm or less and is made of a film harder than the film portion. [2] The sound-proofing structure described in [1], wherein the membrane portion, the support wall portion and the spring portion are all made of either a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity. [3] The sound-proofing structure according to [1] or [2], wherein the membrane portion, the supporting wall portion and the spring portion all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and at a frequency of 1 Hz to 1000 Hz. [4] The sound-proofing structure according to any one of [1] to [3], wherein the membrane portion, the supporting wall portion and the spring portion all have a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. [5] A sound-proofing structure described in any of [1] to [4], wherein the spring portion of the weight portion is located on the side of the weight portion that is attached to the membrane portion, and the mass portion is located on the side opposite to the side of the weight portion that is attached to the membrane portion. [6] The sound-proofing structure according to any one of [1] to [5], wherein the mass portion of the weight portion has a larger volume than the spring portion. [7] A sound-proofing structure according to any one of [1] to [6], wherein the mass portion of the weight portion is made of a material having a higher density than the spring portion. [8] A device having an elastic membrane portion, an elastic support wall portion standing on the membrane portion, a weight portion standing on the membrane portion, and a hard layer laminated on a surface of the membrane portion opposite to a surface on which the support wall portion and the weight portion are provided, 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 spring mass resonator is configured with the membrane portion as a spring portion and the weight portion as a mass portion, A sound-insulating structure, characterized in that the hard layer has a thickness of 1 μm or more and 3000 μm or less and is made of a film harder than the film portion. [9] The sound-proofing structure described in [8], wherein the membrane portion and the supporting wall portion are both made of a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity.

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

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

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

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

[11] , wherein the hard layer has a dynamic storage modulus of 1 MPa or more and 100 GPa or less at 23° C. and a frequency of 1 Hz to 1000 Hz.

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

[12] , 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.

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

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

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

[14] below.

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

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

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

[16] The sound insulation structure according to

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

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

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

[19] The sound-proofing structure described in

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

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

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

[21] A sound-proofing structure as described in any of claims [1] to

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

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

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

[23] The sound-proofing structure according to

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

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

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

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

[24] , 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. [Explanation of symbols]

[0069] 1,6 Sound insulation structure 2 Membrane part 3 Support wall part 3a 1st wall 3b 2nd wall part 4,7 Weight 4a Spring part 4b Mass part 5 Plots 8. Iron Plate 10 hard layer 11 Air Layer 12~15 structure

Claims

1. a film portion having elasticity, a supporting wall portion standing on the film portion and having elasticity, a weight portion standing on the film portion, and a hard layer laminated on a surface of the film portion opposite to a surface on which the supporting wall portion and the weight portion are provided, 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; Each of the weight portions constitutes a spring mass resonator having a spring portion having elasticity and a mass portion having a mass larger than that of the spring portion, A sound-insulating structure, characterized in that the hard layer has a thickness of 1 μm or more and 3000 μm or less and is made of a film harder than the film 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. a film portion having elasticity, a supporting wall portion standing on the film portion and having elasticity, a weight portion standing on the film portion, and a hard layer laminated on a surface of the film portion opposite to a surface on which the supporting wall portion and the weight portion are provided, 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 spring mass resonator is configured with the membrane portion as a spring portion and the weight portion as a mass portion, A sound-insulating structure, characterized in that the hard layer has a thickness of 1 μm or more and 3000 μm or less and is made of a film harder than the film portion.

9. 9. The sound-proofing structure according to claim 8, wherein the membrane portion and the support wall portion are made of any one of a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, and a material that has both rubber elasticity and energy elasticity.

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

11. The sound-proof structure according to claim 10, wherein the film portion and the support wall portion each have a loss tangent of 0.01 or more and 0.50 or less at 23° C. and a frequency range of 1 Hz to 1000 Hz.

12. 9. The sound insulation structure according to claim 1, wherein the hard layer has a dynamic storage modulus of 1 MPa or more and 100 GPa or less at 23° C. and a frequency of 1 Hz to 1000 Hz.

13. 9. 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.

14. 9. The sound insulation structure according to claim 1 or 8, wherein the support wall portion is in the shape of a cylinder having a circular, elliptical or oval cross section defining each of the compartments, or in the shape of a square tube having a polygonal cross section defining each of the compartments.

15. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 9. The sound insulation structure according to claim 1 or 8, wherein:

16. The area of ​​the membrane is 1000 cm 2 The sound insulation structure according to claim 1 or 8, wherein 10 to 1000 of the compartments are provided per unit area.

17. The area of ​​the membrane is 1000 cm 2 17. The sound insulating structure according to claim 16, wherein there are between 50 and 500 of said compartments per one sound insulating structure.

18. 9. 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.

19. 20. The sound insulation structure according to claim 18, wherein the plate thickness of the support wall portion is 1.0 mm or more and 3.0 mm or less.

20. 9. 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.

21. 9. 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.

22. 9. 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.

23. 23. The sound insulation structure according to claim 22, 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.

24. 9. 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.

25. 9. 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.

Images