Sound insulation structure

Abstract

To provide a thin and light sound insulation structure that can obtain sufficient sound insulation properties, and can be easily and stably placed also on a curved mounting surface.SOLUTION: A sound insulation structure 10 includes a sound insulation structure section 1 and a vibration insulation layer 9. The sound insulation structure section 1 has a membrane section 2 having elasticity, a support wall section 3 that is erected in the membrane section 2 and has elasticity, and weight sections 4 erected in the membrane section 2. The membrane section 2 is divided into multiple compartments 5 by a support wall section 3, and one weight section 4 is disposed in one compartment 5. The height H1 of the support wall section 3 is larger than the height H2 of the weight sections 4. Each of the weight sections 4 constitutes a spring mass resonator having a spring section 4a having elasticity, and a mass section 4b having mass larger than that of the spring section 4a. The vibration insulation layer 9 is disposed between an end face in a side opposite to an end face abutting on the membrane sections 2 on the entire surface or a partial surface of the support wall section 3 of the sound insulation structure section 1 and an installation surface 11 in which the sound insulation structure 10 is installed.SELECTED DRAWING: Figure 1

Description

Technical Field

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

Background Art

[0002] In recent years, inside buildings such as apartment houses, office buildings, and hotels, outdoor noise from automobiles, railways, airplanes, ships, etc. outside the building, equipment noise and human voices generated outside the room inside the building are blocked, and tranquility suitable for the use of the room is required. Also, inside vehicles such as automobiles, railways, airplanes, and ships, it is desired to reduce noise by blocking wind noise and engine noise in order to provide a quiet and comfortable space for passengers. Therefore, means for blocking the propagation of noise and vibration from the outside to the inside of buildings and vehicles, and also for blocking the propagation of noise and vibration from the outside to the inside inside buildings and vehicles, that is, a sound insulation structure, is required. In recent years, in buildings, lightweight sound insulation structures have been required due to high-rise construction, etc., and also in vehicles, lightweight sound insulation structures have been required for improving energy efficiency. Examples of sound insulation structures forming sound insulation walls, etc. in vehicles and buildings are disclosed in Patent Documents 1 to 4.

[0003] In the invention described in Patent Document 1, in an acoustic attenuation panel including a rigid frame divided into a plurality of individual cells, a sheet of a flexible material, and a plurality of weights, each weight is fixed to the sheet of the flexible material so that a weight is provided in each cell, and the attenuated sound is controlled by an appropriate selection of the mass of the weights.

[0004] In the invention described in Patent Document 2, in a sound insulation material including an elastic sheet and a support portion that holds the sheet and partitions the sheet into partition portions, the relationship between the rigidity of the sheet in the partition portion and the surface density of the sheet is defined.

[0005] The sound insulation material of the invention described in Patent Document 3 is a structure including a flat substrate portion and a plurality of resonance portions connected to the substrate portion and having a predetermined resonance frequency. Each of the plurality of resonance portions has a weight portion and a connecting portion connecting the weight portion to the substrate portion. In a projection view seen from a direction perpendicular to the substrate portion, the center of gravity of the resonance portion is configured to be located outside the joint region between the substrate portion and the connecting portion.

[0006] The vibration reduction device of the invention described in Patent Document 4 has an acoustic metamaterial mounted on a vehicle body to block vibrations transmitted through the vehicle body, a cross-shaped frame mounted on the vehicle body to partition a certain space into a certain region, and a vibrator configured at a corner portion of each region partitioned by the frame to have respective natural frequencies and block vibrations transmitted from the vehicle body through the frame.

[0007] Patent Document 5 describes a sound reflection structure, which has a substrate and a sound reflection material disposed on the substrate. The sound reflection material includes an elastic sheet and a support portion that supports the sheet and partitions the sheet into partition portions. The surface rigidity and surface density of the sheet in the partition portion have a specific relationship. The sound reflection material and the substrate further have a vibration separation layer disposed between them such that the vibration separation layer is in contact with the sound reflection material without being adhered to the sound reflection material.

[0008] Patent Document 6 describes a soundproof panel, which includes a frame body composed of a pair of first frame members extending in a state of facing each other with a space therebetween, and a pair of second frame members respectively connected between one end portion and the other end portion of the pair of first frame members, a core material and a buffer material laminated on each other in the front and back directions of the frame body, a core body connected between the pair of first frame members, and a pair of plate members provided to cover the front surface and the back surface of the frame body and respectively fixed to the front surface and the back surface of the core body. The core body is arranged such that two portions of the plate member divided by the core body are asymmetric with respect to the core body.

Prior Art Documents

Patent Document

[0009]

Patent Document 1

Patent Document 2

Patent Document 3

Patent Document 4

Patent Document 5

Patent Document 6

Summary of the Invention

Problems to be Solved by the Invention

[0010] The acoustic attenuation panel described in Patent Document 1 has a rigid frame that is not flexible, and vibrations are transmitted to the sheet through this rigid frame, so there is a possibility that sufficient sound insulation cannot be obtained. In addition, when the mounting surface on which the rigid frame is placed is curved or has irregularities, it may not be possible to stably hold the acoustic attenuation panel. In particular, since panels of general vehicles (for example, automobiles) often have curved or irregular portions, it is difficult to simply use them as sound insulation materials for vehicles. In addition, the rigid frame has a large mass, and an increase in mass due to the sound insulation material may be a problem in some cases.

[0011] The sound insulation material described in Patent Document 2 has a high height of the support portion, that is, the height extending in a direction orthogonal to the sheet from the sheet, preferably 25 mm or more. In order to stably support the sheet by such a support portion with a high height, it is preferable that the support portion has rigidity. As a result, there is a possibility that sufficient sound insulation cannot be obtained because vibration is transmitted through the support portion, and it is difficult to place it on a mounting surface having a curved surface or unevenness such as a panel of a vehicle (for example, an automobile). Further, such a support portion with a high height causes an increase in the size and weight of the entire sound insulation material. When placed on a panel of a vehicle or the like, the sound insulation material occupies a large space inside the vehicle, reducing the space efficiency, and there is a concern that it may interfere with the installation of other members or may get in the way of the passengers.

[0012] The sound insulation material described in Patent Document 3 has a resonance portion, which is a functional portion that exhibits a sound insulation effect, exposed without being covered by a support wall or the like. If another member or a human body comes into contact with this resonance portion, there is a possibility that the sound insulation property may decrease or change. Therefore, it is necessary to provide a large space around the resonance portion, resulting in a decrease in space efficiency.

[0013] The vibration reduction device described in Patent Document 4 does not have a film portion and is composed of a plurality of vibrators and a frame connecting them. Therefore, similar to the sound insulation material of Patent Document 3, the vibrator, which is a functional portion that exhibits a sound insulation effect, is exposed. If another member or a human body comes into contact with this vibrator, there is a possibility that the sound insulation property may decrease or change. Further, in order to ensure the minimum structural strength of the vibration reduction device, it is required that the frame has rigidity. As a result, there is a possibility that sufficient sound insulation cannot be obtained because vibration is transmitted through the frame, and it is difficult to place it on a mounting surface having a curved surface or unevenness such as a panel of a vehicle (for example, an automobile).

[0014] The sound reflection structure described in Patent Document 5 exhibits high sound insulation performance at frequencies of about 1.5 kHz to 2.5 kHz, but has poor sound insulation in the low frequency band. Also, the lattice structure is thick, for example, 25 mm, and the sound reflection structure is not thin. Moreover, the adhesion state between the vibration isolation layer of this sound reflection structure and the substrate is unclear, and the sound reflection structure may not be easily installed on curved surfaces or uneven surfaces.

[0015] The sound reflection structure described in Patent Document 6 does not necessarily exhibit high sound insulation in the low frequency band, and the sound reflection structure may not be easily installed on curved surfaces or uneven surfaces. Also, the manufacturing process seems to be relatively complicated.

[0016] Therefore, an object of the present invention is to provide a thin and lightweight sound insulation structure that can obtain sufficient sound insulation and can be easily and stably placed on a curved or uneven mounting surface such as a panel of a building, a mechanical device, or a vehicle (e.g., an automobile), and particularly has good sound insulation in the low frequency region of 1000 Hz or less.

Means for Solving the Problems

[0017] The sound insulation structure of the present invention is a sound insulation structure including a sound insulation structure portion and a vibration insulation layer. The sound insulation structure portion has an elastic film portion, a support wall portion that stands on the film portion and has elasticity, and a weight portion that stands on the film portion. The film portion is divided into a plurality of compartments by the support wall portion, and the weight portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartments where the weight portions are located, one weight portion is arranged in one compartment. The height of the support wall portion extending in the direction perpendicular to the film portion is greater than the height of the weight portion extending in the direction perpendicular to the film portion. Each of the weight portions constitutes a spring mass resonator having an elastic spring portion and a mass portion having a greater mass than the spring portion. The vibration insulation layer is arranged between the end surface on the opposite side of the entire surface or a part of the support wall portion of the sound insulation structure portion in contact with the film portion and the installation surface on which the sound insulation structure is installed. Here, the elasticity referred to means the property that a solid material deformed by an externally applied force returns to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, the case of having at least one of energy elasticity and rubber elasticity (entropy elasticity) is referred to as "having elasticity". The support wall portion and the spring portion may be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the film portion may also be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. The film portion, the support wall portion, and the spring portion may all have a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C. Also, the film portion, the support 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 a frequency of 1 Hz to 1000 Hz at 23°C. Specifically, the elasticity of the film portion, the support wall portion, and the spring portion is evaluated by the dynamic storage modulus (E') obtained by measuring the frequency dependence in the tensile or compression mode of a dynamic viscoelasticity measuring device in accordance with JIS K7244 and obtaining a master curve based on 23°C. The dynamic storage modulus (E') at 23°C and a frequency of 1 Hz to 1000 Hz shall be 0.01 MPa or more and 100 MPa or less. Further, more preferably, both the film portion and the support wall portion may be made of an elastic body having a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent of 0.05 or more and 0.45 or less at 23°C and a frequency of 1 Hz to 1000 Hz. The spring portion of the weight portion is located on the side attached to the film portion of the weight portion, and the mass portion may be located on the side opposite to the side attached to the film portion of the weight 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.

[0018] Another sound insulation structure of the present invention is a sound insulation structure including a sound insulation structure portion and a vibration insulation layer. The sound insulation structure portion has an elastic film portion, a support wall portion standing on the film portion and having elasticity, and a weight portion standing on the film portion. The film portion is divided into a plurality of compartments by the support wall portion, and the weight portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartment where the weight portion is located inside, one weight portion is arranged in one compartment. The height of the support wall portion extending in the direction perpendicular to the film portion is larger than the height of the weight portion extending in the direction perpendicular to the film portion. The film portion serves as a spring portion, and the weight portion serves as a mass portion to constitute a spring-mass resonator. The vibration insulation layer is arranged between the entire surface or a part of the support wall portion of the sound insulation structure portion, the end surface opposite to the end surface in contact with the film portion, and the installation surface on which the sound insulation structure is installed. The support wall portion may be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the film portion may also be made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. Both the film portion and the support wall portion may have a dynamic storage modulus at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 MPa or more and 100 MPa or less. Also, both the film portion and the support wall portion may be made of an elastomer having a loss tangent at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 or more and 0.50 or less. More preferably, both the film portion and the support wall portion may be made of an elastomer having a dynamic storage modulus (E’) at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.05 MPa or more and 50 MPa or less, and a loss tangent at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.05 or more and 0.45 or less.

[0019] The sound insulation structure of the present invention described above and another sound insulation structure may have the following configuration. The vibration insulation layer may be disposed between the end face of the support wall portion located at the outermost periphery of the sound insulation structure portion, which is opposite to the end face in contact with the film portion, and the installation surface. Alternatively, the vibration insulation layer may be disposed between the entire sound insulation structure portion and the installation surface. The vibration insulation layer may be made of a resin material having rubber elasticity or a porous material. The vibration insulation layer may be made of a resin material having a dynamic storage modulus at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 MPa or more and 100 MPa or less, and a loss tangent at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 or more and 0.50 or less. Alternatively, the vibration insulation layer may be made of a porous material having a density of 0.001 g / cm 3 or more and 0.5 g / cm 3 or less. The thickness of the vibration insulation layer may be 0.5 mm or more and 10 mm or less. The support wall portion may include a plurality of first wall portions extending in a first direction parallel to the film portion while extending in a direction orthogonal to the film portion, and a plurality of second wall portions extending in a second direction orthogonal to the first direction while extending in a direction orthogonal to the film portion. The support wall portion may be a cylindrical shape having a circular, elliptical or oval cross-sectional shape defining each of the compartments, or a square tube shape having a polygonal cross-sectional shape defining each of the compartments, specifically a cross-sectional shape of a square, a regular pentagon or a regular hexagon. The area of each of the compartments may be 100 mm 2 or more and 1000 mm 2 or less. There may be provided 10 or more and 1000 or less of the compartments per 1000 cm 2 of the area of the film portion, and it is more preferable that 50 or more and 500 or less of the compartments are provided. The plate thickness of the support wall portion may be 0.5 mm or more and 5.0 mm or less, and it is more preferable that it is 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 the direction orthogonal to the film portion may be 5 mm or more and 20 mm or less. The height of the support wall portion extending in the direction orthogonal to the film portion may be 5 mm or more and 20 mm or less, and the height may be partially different. The height of the weight portion extending in the direction orthogonal to the film portion may be 1 mm or more. The durometer A hardness of the film portion may be 50 or more, and the durometer A hardness of the support wall portion may be 1 or more and 90 or less. The durometer A hardness can be obtained by measuring in accordance with JIS K 6253-3.

Advantages of the Invention

[0020] According to the present invention, there is provided a thin and lightweight sound insulation structure that can obtain sufficient sound insulation performance and can be easily and stably placed on a curved or uneven mounting surface such as a panel of a building, a mechanical device, or a vehicle (e.g., an automobile), and in particular, a sound insulation structure having good sound insulation performance in a low frequency region of 1000 Hz or less can be provided.

Brief Description of the Drawings

[0021]

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Mode for Carrying Out the Invention

[0022] Hereinafter, embodiments 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 10 according to a first embodiment of the present invention, and FIG. 1(B) is a cross-sectional view taken along line A-A of FIG. 1(A) and turned upside down. The sound insulation structure 10 includes a sound insulation structure part 1 and a vibration insulation layer 9. The sound insulation structure part 1 has an elastic film part 2, a support wall part 3 and a weight part 4 standing on the film part 2. The vibration insulation layer 9 is disposed at least between at least a part of the end surface of the support wall part 3 of the sound insulation structure part 1 opposite to the end surface in contact with the film part 2 and the installation surface 11 on which the sound insulation structure 10 is installed.

[0023] The sound insulation structure portion 1 of the sound insulation structure 10 of this embodiment will be described. FIG. 2(A) is a perspective view of the sound insulation structure portion 1 of this embodiment, and FIG. 2(B) is a cross-sectional view taken along line A-A of FIG. 2(A) and inverted vertically. The sound insulation structure portion 1 has an elastic sheet-like film portion 2, a support wall portion 3 standing substantially vertically from the film portion 2, and a weight portion 4 standing substantially vertically from the film portion 2. The film portion 2 is divided into a plurality of compartments (unit structures) 5 by the support wall portion 3. The weight portions 4 are respectively located inside the plurality of compartments 5, and in the compartment 5 where the weight portion 4 is located, one weight portion 4 is located in one compartment 5. FIG. 3(A) is an exploded perspective view of one compartment 5 of the sound insulation structure portion 1, and FIG. 3(B) is an exploded front view thereof. The height H1 of the support wall portion 3 extending from the film portion 2 in a direction orthogonal to the film portion 2 is greater than the height H2 of the weight portion 4 extending from the film portion 2 in a direction orthogonal to the film portion 2. Each of the weight portions 4 constitutes a spring-mass resonator having an elastic spring portion 4a and a mass portion (mass part) 4b having a mass greater than that of the spring portion 4a. The elasticity referred to here means the property of a solid substance deformed by an externally applied force to return to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, the case of having at least one of energy elasticity and rubber elasticity (entropy elasticity) is referred to as "having elasticity".

[0024] The support wall portion 3 of the present embodiment 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 orthogonal to the first direction D1. The plurality of first wall portions 3a are arranged in parallel, and the plurality of second wall portions 3b are arranged in parallel. The first wall portion 3a and the second wall portion 3b are integrated at the intersection. In this way, the plurality of first wall portions 3a and the plurality of second wall portions 3b constitute a lattice structure, and a plurality of compartments 5 having a square planar shape partitioned by the first wall portion 3a and the second wall portion 3b are arranged in a matrix. In other words, the support wall portion 3 has a structure in which a plurality of square prism-shaped members having a square cross-sectional shape defining individual compartments 5 are arranged side by side. The support wall portion 3 is preferably made of a flexible material such as rubber, elastomer, or resin foam. The flexible material mentioned here is any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0025] A portion of the weight portion 4 of the present embodiment on the side attached to the film portion 2 is a spring portion 4a, and a portion on the side opposite to the side attached to the film portion 2 is a mass portion 4b having a larger mass than the spring portion 4a. In the examples shown in FIGS. 1 to 4, the spring portion 4a and the mass portion 4b have the same shape and the same dimensions, but different materials. The spring portion 4a is made of a flexible material, and the mass portion 4b is made of a material having a higher density than the material constituting the spring portion 4a. A spring-mass resonator is configured in which the spring portion 4a functions as a spring and the mass portion 4b functions as a mass. Note that, together with the spring portion 4a of the weight portion 4, the film portion 2 may also function as a part of the spring of the spring-mass resonator. Further, the air in the space surrounded by the film portion 2 and the support wall portion 3 may function as a part of the spring (air spring) of the spring-mass resonator. The spring portion 4a is also preferably made of any one of a flexible material, that is, a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0026] According to the sound insulation structure portion 1 of the present embodiment, the vibration of the film portion 2 is controlled by the action of the 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, a frequency of 1000 Hz or less which is the main frequency band of road noise in an automobile), the film vibration is significantly reduced. As a result, the radiated sound from the film portion 2 becomes small and high sound insulation performance is exhibited.

[0027] The partition 5 of the sound insulation structure portion 1 of the present embodiment is preferably provided in a number of 10 or more and 1000 or less per 1000 cm of the area of the film portion 2, and more preferably 50 or more and 500 or less. Since there are 10 or more partitions 5 per 1000 cm of the area of the film portion 2, the entire sound insulation structure portion 1 can be divided into a plurality of partitions 5 and the sound insulation effect can be exhibited for each partition, and the sound insulation performance of the entire sound insulation structure portion 1 is improved. Also, since the number of partitions 5 is 1000 or less per 1000 cm of the area of the film portion 2, an increase in the weight of the entire sound insulation structure portion 1 can be suppressed. The area of the planar shape of each partition 5 is preferably 100 mm 2 or more and 1000 mm 2 or less, and more preferably 200 mm 2 or more and 800 mm 2 or less. Since the area of the planar shape of each partition 5 is 100 mm 2 or more, it is easy to arrange the weight portion 4 inside. On the other hand, since the area is 1000 mm 2 or less 2 the weight increase of the entire sound insulation structure portion 1 can be suppressed. Since the area of the planar shape of each partition 5 is 100 mm 2 or more, it is easy to arrange the weight portion 4 inside. On the other hand, since the area is 1000 mm 2Therefore, since it is as follows, the effect of the weight portion 4 on the film portion 2 is large, and high sound insulation performance can be obtained. The height of the entire sound insulation structure portion 1 in the direction orthogonal to the film portion 2 is preferably 5 mm or more and 20 mm or less. Since the height of the entire sound insulation structure portion 1 is 5 mm or more, the weight portion 4 can have a sufficient height as a spring mass resonator, and since the height is 20 mm or less, an increase in the weight of the entire sound insulation structure portion 1 can be suppressed. Note that each drawing schematically shows each section 5, the support wall portion 3, etc., and there are cases where the number and area of the section 5 and the height of the support wall portion 3 are not strictly and accurately shown, or cases where they are not unified in each drawing. However, it is preferable that the number and area of the section 5 and the height of the support wall portion 3 are appropriately designed so as to fall within the above-described numerical ranges, respectively.

[0028] In the present embodiment, the film portion 2, the support wall portion 3, and the spring portion 4a of the sound insulation structure portion 1 are all made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C and a loss tangent (tanδ) of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. Preferably, the dynamic storage modulus (E') is 0.05 MPa or more and 50 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C, and the loss tangent (tanδ) is 0.05 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. The dynamic storage modulus (E') and the loss tangent (tanδ) are obtained by creating a master curve based on 23°C using a dynamic viscoelasticity tester. Since the dynamic storage modulus (E') at a frequency of 1 Hz to 1000 Hz at 23°C is 0.01 MPa or more, the sound insulation performance in the target frequency band is good, and the shape retention of the film portion 2 and the support wall portion 3 is good. Since the dynamic storage modulus (E') at a frequency of 1 Hz to 1000 Hz at 23°C is 100 MPa or less, the vibration in the frequency band to be sound-insulated is good, the sound insulation structure portion 1 does not become rigid, and the installability is also good. The film portion 2 and the support wall portion 3 may be formed of the same material or different materials. The film portion 2 is preferably made of any one of a flexible material, that is, a material having no energy elasticity and having rubber elasticity, a material having no rubber elasticity and having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0029] The diaphragm part 2 is preferably a relatively hard elastic membrane because the hammer part 4 is attached thereto. The dynamic storage elastic modulus (E') of the diaphragm part 2 is preferably 15 MPa or more, the thickness (membrane thickness) is preferably 0.1 mm or more and 3.0 mm or less, and more preferably about 0.5 mm. When the thickness of the diaphragm part 2 is 0.1 mm or more, a sufficient thickness can be ensured, so that it is easy to handle. When the thickness of the diaphragm part 2 is 3.0 mm or less, an increase in the thickness and weight of the entire sound insulation structure part 1 can be suppressed, and the entire sound insulation structure part 1 does not become too hard and the installability is good. The material of the diaphragm part 2 preferably has a durometer A hardness of 50 or more according to JIS K6253, and more preferably 70 or more. By setting the durometer A hardness of the diaphragm part 2 within the above range, deterioration of the vibration of the diaphragm part 2 is prevented, and the sound insulation performance in the frequency band to be sound-insulated becomes good. And the rigidity (axial rigidity) k of the diaphragm part 2 is expressed as k = E'×A / L from the dynamic storage elastic modulus E', the cross-sectional area A of the diaphragm part 2, and the thickness L of the diaphragm part 2. When the area of the diaphragm part 2 to be evaluated for rigidity is 1000 cm 2 when it is, the rigidity k is preferably 10 6 N / mm or more and 10 9 N / mm or less, and more preferably 3×10 6 N / mm or more and 10 8 N / mm or less. When the area of the diaphragm part 2 is 1000 cm 2 when it is, the rigidity of 10 6 N / mm or more can suppress deterioration of the vibration of the diaphragm part 2, and the sound insulation performance in the frequency band to be sound-insulated becomes good. When the area of the diaphragm part 2 is 1000 cm 2 when it is, the rigidity of 10 9 N / mm or less makes the sound insulation structure part 1 flexible and the installability good. Further, the bending rigidity K of the diaphragm part 2 is expressed as K = E'×I from the dynamic storage elastic modulus E' and the second moment of area I. The second moment of area I is calculated as I = b×h 3 / 12 from the thickness h and the width b of the diaphragm part 2. When the area of the diaphragm part 2 to be evaluated is 1000 cm 2 when it is, the bending rigidity K is 1 N / mm 2 or more and 10 5 N / mm2 It is preferably the following, 10 N / mm 2 or more and 5×10 4 N / mm 2 or less is more preferable. When the area of the film portion 2 is 1000 cm 2 the bending rigidity K being 1 N / mm 2 or more enables good vibration of the film portion 2 and can suppress deterioration of the sound insulation property in the frequency band to be sound-insulated. When the area of the film portion 2 is 1000 cm 2 the bending rigidity K being 10 5 N / mm 2 or less makes the sound insulation structure portion 1 flexible and improves the installability. The cross-sectional shape of the film portion 2 is not particularly limited and may be flat or may have irregularities.

[0030] Examples of the material of the diaphragm portion 2 include crosslinked (vulcanized) rubber, thermoplastic elastomer, and plastic. Examples of the 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-propylene rubber (EPM), ethylene-propylene-diene rubber (EPDM), and ethylene-butene-diene rubber (EBDM) such as ethylene·α-olefin·non-conjugated polyene copolymers, chlorosulfonated polyethylene (CSM), chlorinated polyethylene (CM), acrylic rubber (ACM), ethylene-acrylic rubber (AEM), ethylene-vinyl acetate rubber (EVA), epichlorohydrin rubber (CO, ECO), polysulfide rubber (T), silicone rubber (Q) such as methyl vinyl silicone rubber (VMQ) and fluorinated silicone rubber (FVMQ), urethane rubber (U), and various rubber materials such as fluororubber (FKM) crosslinked (vulcanized). These crosslinked (vulcanized) rubbers can be used alone or in combination of two or more. Note that as the crosslinking (vulcanizing) method, for example, a method of crosslinking (vulcanizing) by heating using an organic peroxide, phenol resin, oxime compound, sulfur, sulfur-based compound, or polyamine compound as a crosslinking agent (vulcanizing agent), or a method of crosslinking by irradiating with an electron beam can be mentioned. Note that the crosslinked (vulcanized) rubber may generally be compounded with various known compounding agents (reinforcing agents such as carbon black and silica, fillers such as calcium carbonate, softening agents such as paraffin oil and plasticizer, processing aids, antioxidants, light stabilizers, flame retardants, antifungal agents, acid acceptors, silane coupling agents, antistatic agents, ultraviolet absorbers, etc.) used as rubber compounding agents. These crosslinked (vulcanized) rubbers, crosslinking agents (vulcanizing agents), and compounding agents may be made of biomass raw materials.

[0031] Examples of the thermoplastic elastomer include olefin-based thermoplastic elastomers, styrene-based thermoplastic elastomers, polyester-based thermoplastic elastomers, polyvinyl chloride-based thermoplastic elastomers, ethylene-vinyl acetate-based thermoplastic elastomers, and the like. Examples of the plastic include polyethylene, polypropylene, polystyrene, polyethylene terephthalate, polyvinyl chloride, or a composite resin containing them. These thermoplastic elastomers and plastics may be made of biomass raw materials.

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

[0033] The support wall portion 3 is preferably made of a soft and flexible material within a range capable of supporting the film portion 2. The plate thickness of the support wall portion 3 is preferably 0.5 mm or more and 5.0 mm or less, and more preferably 1.0 mm or more and 3.0 mm or less. When the plate thickness of the support wall portion 3 is 0.5 mm or more, the shape retention of the sound insulation structure portion 1 becomes good. When the plate thickness of the support wall portion 3 is 5.0 mm or less, the vibration of the film portion 2 is good, the sound insulation performance in the frequency band to be sound-insulated is good, and an increase in the weight of the entire sound insulation structure portion 1 can be suppressed. The height extending in the direction orthogonal to the film portion 2 of the support wall portion 3 is preferably 5 mm or more and 20 mm or less, and more preferably 10 mm or more and 20 mm or less. The support wall portion 3 may be partially different in height. When the height of the support wall portion 3 is partially different, the higher portion 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. Since the height of the support wall portion 3 is not too low, the weight portion 4 can have a sufficient height as a spring mass resonator. Since the height of the support wall portion 3 is not too high, the overall weight can be reduced. The material of the support wall portion 3 preferably has a durometer A hardness of 1 or more and 90 or less according to JIS K6253, and more preferably 10 or more and 70 or less. When the durometer A hardness of the support wall portion 3 is 1 or more, the shape retention of the sound insulation structure portion 1 can be maintained. When the durometer A hardness of the support wall portion 3 is 90 or less, vibration from the support wall portion 3 can be prevented from being transmitted to the film portion 2 and deteriorating the sound insulation performance, and the sound insulation structure portion 1 becomes flexible and the installability becomes good. And the rigidity k of the support wall portion 3 is expressed as k = E'×A / L from the dynamic storage modulus of elasticity E', the cross-sectional area A of the support wall portion 3, and the height L of the support wall portion 3. When the area of the support wall portion 3 to be evaluated for rigidity is 1000 cm 2 When it is, the rigidity k is preferably 10 N / mm or more and 10 6 N / mm or less, and more preferably 10 2 N / mm or more and 10 5 N / mm or less. When the area of the support wall portion 3 is 1000 cm 2When the rigidity k is 10 N / mm or more, the shape retention of the sound insulation structure portion 1 can be maintained. When the area of the support wall portion 3 is 1000 cm 2 When the rigidity k is 10 6 N / mm or less, vibration from the support wall portion 3 is prevented from being transmitted to the film portion 2, preventing deterioration of the sound insulation performance, and the sound insulation structure portion 1 is not rigid and has good installability.

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

[0035] The material of the spring portion 4a of the weight portion 4 is a flexible material such as crosslinked (vulcanized) rubber, thermoplastic elastomer, resin foam, etc. The crosslinked (vulcanized) rubber, thermoplastic elastomer, and resin foam may be the same as the materials listed as the material of the support wall portion 3. Specifically, the material of the spring portion 4a of the weight portion 4 is preferably ethylene-propylene-diene rubber, urethane rubber, silicone rubber, thermoplastic olefin-based elastomer, thermoplastic styrene-based elastomer, thermoplastic polyurethane, polyurethane foam, etc. These materials may be made of biomass raw materials.

[0036] The material of the mass portion 4b is not particularly limited, and it may be made of resin, metal, or the like. The mass of the mass portion 4b is larger than that of the spring portion 4a, and it has a mass of, for example, 0.1 g or more and 2.0 g or less. Preferably, the mass portion 4b has a mass that is at least twice the mass of the spring portion 4a. By having the weight of the mass portion 4b be at least twice the mass of the spring portion 4a, the weight portion 4 can be sufficiently resonated in the frequency range to be sound-insulated, and a good sound-insulating effect can be obtained. When the material of the mass portion 4b is resin, the resin may be made of biomass raw materials.

[0037] The spring constant (rigidity) of the spring portion 4a is determined based on the mass of the mass portion 4b so that the resonance frequency matches the frequency that is the main sound-insulation target. As an example, when the mass of the mass portion 4b is 1.0 g and the frequency that is the main sound-insulation target is 1000 Hz or less, the spring constant of the spring portion 4a is 0.5 N / mm or more and 100 N / mm or less, and more preferably 1 N / mm or more and 50 N / mm or less.

[0038] With such a configuration, each of the film portion 2, the support wall portion 3, and the weight portion 4 is relatively lightweight, and the dimension in the direction orthogonal to the film portion 2 is relatively small. Thus, although the sound-insulating structure portion 1 of the present embodiment is lightweight and thin, as described above, high sound insulation can be obtained in a specific frequency range (for example, a frequency of 1000 Hz or less, which is the main frequency band of road noise in an automobile). And the support wall portion 3 made of a flexible material can be easily and stably installed on a flat mounting surface, a curved mounting surface, or a mounting surface having irregularities without being fixed by adhesion or the like via the vibration insulation layer 9.

[0039] The sound insulation structure 10 of the present embodiment is such that the end face of the support wall portion 3 of the sound insulation structure portion 1 having the configuration described above, which is opposite to the end face in contact with the film portion 2, is disposed on the installation surface (for example, a panel of a vehicle such as an automobile) 11 schematically shown in FIG. 1(B). However, a thin and flexible vibration insulation layer 9 is interposed between the support wall portion 3 located at the outermost periphery of the sound insulation structure portion 1 and the installation surface 11. The vibration insulation layer 9 is made of a resin material having rubber elasticity (for example, an elastomer or rubber) or a porous material (paper, batting, foam, felt, glass wool, non-woven fabric, etc.), and these materials may be made of biomass raw materials. The vibration insulation layer 9 preferably has a thickness of 0.5 mm to 10 mm. When the thickness of the vibration insulation layer 9 is 0.5 mm or more, solid propagation from the iron plate 8 to the sound insulation structure 10 can be suppressed. Further, when the thickness of the vibration insulation layer 9 is 10 mm or less, the entire sound insulation structure 10 can be made thin with a thickness of 25 mm or less and an increase in weight can be suppressed. When the vibration insulation layer 9 is made of a resin material having rubber elasticity, similar to the film portion 2 and the support wall portion 3, the dynamic storage elastic modulus (E') at 23°C and frequencies from 1 Hz to 1000 Hz is preferably 0.01 MPa or more and 100 MPa or less, and the loss tangent (tanδ) at 23°C and frequencies from 1 Hz to 1000 Hz is preferably 0.01 or more and 0.50 or less. When the vibration insulation layer 9 is made of a porous material, the density is preferably 0.001 g / cm 3 or more and 0.5 g / cm 3 or less. When the density of the vibration insulation layer 9 is 0.001 g / cm 3 or more, the sound insulation structure 10 can be self-standing and has good installability. Further, when the density of the vibration insulation layer 9 is 0.5 g / cm 3 or less, an increase in weight can be suppressed. The vibration insulation layer 9 may be fixed to the end face of the support wall portion 3 opposite to the end face in contact with the film portion 2 by adhesion or the like, or may not be fixed.

[0040] In addition to the sound insulation effect of the sound insulation structure portion 1 described above, the sound insulation structure 10 of the present embodiment can separate vibrations from the installation surface 11 by the thin vibration insulation layer 9 disposed between the sound insulation structure portion 1 and the installation surface 11, and can achieve good sound insulation without impairing the function of the sound insulation structure portion 1.

[0041] In the example shown in FIG. 1, the vibration insulation layer 9 is provided along the support wall portion 3 located on the outermost periphery of the sound insulation structure portion 1, but the configuration is not limited thereto. Although not shown, a part of the vibration insulation layer 9 along the support wall portion 3 located on the outermost periphery may be missing. Further, the vibration insulation layer 9 may extend to positions other than the position facing the support wall portion 3 located on the outermost periphery of the sound insulation structure portion 1. FIG. 4(A) shows a perspective view of the sound insulation structure 10 of a modified example of the present embodiment, and FIG. 4(B) shows a cross-sectional view taken along line A-A of FIG. 4(A) and turned upside down. In this modified example, a large-area vibration insulation layer 9 covering the entire sound insulation structure portion 1 is provided. Thus, the vibration insulation layer 9 may be provided in part or in whole of the portion where the sound insulation structure portion 1 and the installation surface face each other, and can be sufficiently exhibited without impairing the sound insulation effect of the sound insulation structure portion 1.

[0042] Figures 5 to 7 show still other modified examples of the present embodiment. In the modified examples shown in Figures 5 to 7, the weight portions 4 of the sound insulation structure portion 1 are different from each other, and the other configurations are common. Figure 5(A) is a perspective view of the sound insulation structure portion 1 of the sound insulation structure 10 of still other modified examples of the present embodiment, and Figure 5(B) is a cross-sectional view taken along line A-A of Figure 5(A) and inverted upside down. Figure 6(A) is a cross-sectional view of the sound insulation structure portion 1 of the sound insulation structure 10 of still other modified examples, and Figure 6(B) is a perspective view of the weight portion 4 of the sound insulation structure portion 1. Figure 7(A) is a cross-sectional view of the sound insulation structure portion 1 of the sound insulation structure 10 of still other modified examples, and Figure 7(B) is a perspective view of the weight portion 4 of the sound insulation structure portion 1. In the modified example shown in Figures 5(A) and 5(B), the spring portion 4a is a small-diameter cylindrical shape, and the mass portion 4b is a large-diameter cylindrical shape. In the modified example shown in Figures 6(A) and 6(B), the spring portion 4a is an elongated cylindrical shape, the mass portion 4b is a spherical shape, and the diameter of the cross-sectional shape of the cylindrical spring portion 4a is smaller than the diameter of the spherical mass portion 4b. In the modified example shown in Figures 7(A) and 7(B), the spring portion 4a is a frustum of a cone shape, the mass portion 4b is a cylindrical shape, and the diameter of the smallest portion of the frustum of a cone-shaped spring portion 4a substantially coincides with the diameter of the cylindrical mass portion 4b. In the modified examples shown in Figures 5 to 6, the mass portion 4b has a larger volume than the spring portion 4a. Therefore, even if the spring portion 4a and the mass portion 4b are formed of the same material, the mass portion 4b has a larger mass than the spring portion 4a and can constitute a spring-mass resonator. However, in this modified example, the spring portion 4a and the mass portion 4b may be formed of different materials, and the mass portion 4b may have a larger mass than the spring portion 4a. On the other hand, in the modified example shown in Figure 7, the spring portion 4a has a larger volume than the mass portion 4b. In this case, the mass portion 4b is formed of a material having a higher density than the spring portion 4a, and the mass portion 4b has a larger mass than the spring portion 4a and can constitute a spring-mass resonator. When the spring portion 4a is a frustum of a cone shape that tapers in a direction away from the film portion 2 as in the modified example shown in Figure 7, the mold release property from the mold when the film portion 2 and the spring portion 4a are integrally formed is good. The shape and dimensions of the weight portion 4 of the present invention are not limited, and the shapes shown in Figures 3 to 7 and various other shapes not shown can be adopted.The hammer portion 4 is formed in any shape and dimensions selected to satisfy the performance of the spring mass resonator required for sound insulation and to be accommodated within the partition 5. Although not shown, in the modified examples shown in FIGS. 5 to 7, the vibration insulation layer 9 has the shape shown in FIGS. 1 and 6 or any other arbitrary shape.

[0043] In the present embodiment, the spring portion 4a and the mass portion 4b of the hammer portion 4 are made to differ in either one or both of the material and volume, so that the mass of the mass portion 4b is made larger than that of the spring portion 4a to constitute a spring mass resonator, and a sufficient sound insulation effect is obtained. 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 capable of exhibiting a sufficient sound insulation effect can be constituted. As long as the mass of the mass portion 4b can be made larger than that of the spring portion 4a to such an extent that a spring mass resonator capable of exhibiting a sufficient sound insulation effect is constituted, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b can be freely selected. However, since the spring portion 4a functions as a spring, it needs to be formed from a flexible material.

[0044] [Second Embodiment] FIG. 8(A) is a perspective view of the sound insulation structure portion 6 of the sound insulation structure 10 according to the second embodiment of the present invention, and FIG. 8(B) is a cross-sectional view taken along line A-A of FIG. 8(A) and turned upside down. The sound insulation structure portion 6 of the present embodiment has a hammer portion 7 having a single structure that is not divided into a spring portion and a mass portion, and a spring mass resonator is constituted in which the entire hammer portion 7 functions as a mass portion and the film portion 2 functions as a spring portion. As an example, the mass of the hammer portion 7 is about 0.1 g to 2.0 g. The material of the hammer portion 7 is not limited, and it is formed from, for example, a synthetic resin or metal. Since the other configurations are the same as those of the first embodiment described above, the description thereof is omitted. Also in the sound insulation structure portion 6 of the present embodiment, the membrane vibration is controlled by the action of the spring mass resonator constituted by the hammer portion 7 and the membrane portion 2, and in a specific frequency range (for example, 1000 Hz or less), the membrane vibration is significantly reduced and high sound insulation performance is exhibited. In addition, together with the film portion 2, the air in the space surrounded by the film portion 2 and the support wall portion 3 may function as a part of the spring (air spring) of the spring mass resonator.

[0045] In this embodiment, both the film portion 2 and the support wall portion 3 preferably have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C, and preferably have a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. Further, both the film portion 2 and the support wall portion 3 of this embodiment preferably have a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C, and a loss tangent (tanδ) of 0.05 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C.

[0046] Also, the support wall portion 3 of this embodiment is made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the film portion 2 of this embodiment is also made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0047] In the sound insulation structure 10 of this embodiment as well, a vibration insulation layer 9 similar to that of the first embodiment is provided. The vibration insulation layer 9 is disposed at least between at least a part of the end face of the support wall portion 3 of the sound insulation structure portion 6 opposite to the end face in contact with the film portion 2 and the installation surface 11 (see FIG. 1(B)) on which the sound insulation structure 10 is installed. As an example, the vibration insulation layer 9 may be provided along the support wall portion 3 located at the outermost periphery of the sound insulation structure portion 1 as in the configuration shown in FIG. 1, or may be provided so as to cover the entire sound insulation structure portion 1 as in the configuration shown in FIG. 4. Further, the vibration insulation layer 9 may be formed in various other planar shapes.

[0048] Although not shown, in a modification of the second embodiment of the present invention, the weight portion 7 has a frustum of a cone that tapers in a direction away from the film portion 2. In this configuration, the mold releasability is good when the film portion 2 and the weight portion 7 are integrally formed. In the present embodiment, the shape of the weight portion 7 can be arbitrarily determined and is not particularly limited. Also in this modification, it has a vibration insulating layer 9 having the shape shown in FIGS. 1 and 6 or any other arbitrary shape.

[0049] In any of the first and second embodiments, the film portion 2 and the support wall portion 3 can be formed by integral molding or two-color molding by injection molding, compression molding, press molding, extrusion molding, transfer molding, casting, etc. of the above-described materials. Further, at least a part of the weight portions 4 and 7 may be formed together with the film portion 2 and the support wall portion 3 by integral molding, two-color molding, insert molding, etc. of the above-described materials. However, the sound insulation structure portions 1 and 6 may be assembled by forming the film portion 2, the support wall portion 3, and the weight portions 4 and 7 separately and then joining them to each other by adhesion or heat fusion.

[0050] In the configurations of the sound insulation structure parts 1 and 6 described above, as shown in FIGS. 9(A) and 9(B), the support wall part 3 includes a plurality of first wall parts 3a extending in a first direction D1 parallel to the film part 2 and a plurality of second wall parts 3b extending in a second direction D2 orthogonal to the first direction D1, and the planar shape of each compartment 5 is square. In other words, the support wall part 3 has a square tube shape with a square cross-sectional shape that defines each individual compartment 5, and a large number of such square tube-shaped support wall parts 3 are arranged side by side, with the support wall parts 3 of adjacent compartments 5 integrated. However, it is not limited to such a configuration. For example, although not shown, the planar shape of each compartment 5 may be triangular, and the support wall part 3 may have a triangular tube shape with a triangular cross-sectional shape that defines each individual compartment 5. Also, although not shown, the planar shape of each compartment 5 may be pentagonal, and the support wall part 3 may have a pentagonal tube shape with a pentagonal cross-sectional shape that defines each individual compartment 5. As shown in FIGS. 10(A) and 10(B), the planar shape of each compartment 5 may be hexagonal, and the support wall part 3 may have a hexagonal tube shape with a hexagonal cross-sectional shape that defines each individual compartment 5, constituting a so-called honeycomb structure. Further, although not shown, the planar shape of each compartment 5 may be circular, and the support wall part 3 may have a cylindrical shape with a circular cross-sectional shape that defines each individual compartment 5. In the case of a configuration where the planar shape of each compartment 5 is pentagonal or circular, a gap is generated between the compartments 5, so it is preferable to determine the shape and dimensions of the support wall part 3 so that the gap becomes smaller, and it is preferable that the film part 2 spreads to close the gap. In the case of a configuration where the planar shape of each compartment 5 is triangular, square, or hexagonal, no gap is generated between the compartments 5. Further, each compartment 5 may have various shapes not shown, for example, rectangular, parallelogram, trapezoid, polygon with seven or more sides, ellipse, oval, etc., or may have an irregular shape. The support wall part 3 is formed in a shape and dimensions corresponding to the planar shape of each compartment 5.

[0051] As the part where the sound insulation structure 10 of the present invention is installed in an automobile, in the engine compartment, there are an engine head cover, an engine body cover, a hood insulator, a dash front insulator, the wall of an air box, a cleaner of an air intake, a dust side duct, an under cover, etc.; in the cabin, there are a dash insulator, a dash panel, a floor carpet (floor silencer), a spacer, a door trim of a door, the inside of the door trim, an instrument panel, an instrument center box, an instrument upper box, a housing of an air conditioner, a roof trim, the inside of the roof trim, a sun visor, a rear seat air conditioner duct, a cooling duct of a battery cooling system in a battery-mounted vehicle, a cooling fan, a trim of a center console, the inside of the console, a parcel trim, a parcel panel, a headrest of a seat, a seat back of a front seat, a seat back of a rear seat, etc.; in the trunk, there are a trim of a trunk side, the inside of the trim, a drafter cover, etc. Further, the sound insulation structure 10 of the present invention can also be installed inside the skeleton of an automobile or between panels, and furthermore, it can also be installed on an under cover under the floor, a fender protector, a back door, a wheel cover, an aerodynamic cover of a suspension, etc. located outside the vehicle.

Example

[0052] The specific examples and comparative examples of the present invention will be described below. [Example 1] The sound insulation structure 10 of Example 1 of the present invention has the same structure as the first embodiment shown in FIG. 1. The film part 2 is made of an elastic body having a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C and a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. More specifically, the film part 2 of this example has a dynamic storage elastic modulus (E') of 20.4 MPa at a frequency of 1 Hz at 23°C, a loss tangent (tanδ) of 0.12, a dynamic storage elastic modulus (E') of 23.0 MPa at a frequency of 10 Hz at 23°C, a loss tangent (tanδ) of 0.13, a dynamic storage elastic modulus (E') of 25.4 MPa at a frequency of 100 Hz at 23°C, a loss tangent (tanδ) of 0.16, a dynamic storage elastic modulus (E') of 28.8 MPa at a frequency of 1000 Hz at 23°C, a loss tangent (tanδ) of 0.14, a durometer A hardness of 70 according to JIS K6253, and is made of EPDM (ethylene-propylene-diene rubber) with a film thickness of 0.5 mm. When the planar shape of this film part 2 is a square with an area of 1000 cm 2 the bending stiffness K is 67.2 N / mm 2 When the planar shape is a square with an area of 400 cm 2 the bending stiffness K is 42.5 N / mm 2 If a film part 2 made of the same material as this film part 2, with a film thickness of 3 mm and a planar shape of a square with an area of 1000 cm 2 is formed, its bending stiffness K is about 1.5×10 4 N / mm 2 is.

[0053] The support wall portion 3 of this embodiment is made of an elastic body having a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C and a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. More specifically, the support wall portion 3 of this embodiment has a dynamic storage modulus (E') of 13.2 MPa and a loss tangent (tanδ) of 0.12 at a frequency of 1 Hz at 23°C, a dynamic storage modulus (E') of 15.0 MPa and a loss tangent (tanδ) of 0.14 at a frequency of 10 Hz at 23°C, a dynamic storage modulus (E') of 17.4 MPa and a loss tangent (tanδ) of 0.17 at a frequency of 100 Hz at 23°C, a dynamic storage modulus (E') of 20.2 MPa and a loss tangent (tanδ) of 0.16 at a frequency of 1000 Hz at 23°C, a durometer A hardness of 65 according to JIS K6253, a plate thickness of 1.6 mm, and is made of EPDM with a height in the direction orthogonal to the film portion 2 of 10 mm. The weight portion 4 is cylindrical with a diameter of 6 mm and a height (dimension in the direction orthogonal to the film portion 2) of 6 mm. The compartment 5 defined by the support wall portion 3 is square-shaped with sides of 25 mm × 25 mm, and there are 49 compartments 5 in the 200 mm × 200 mm square region (evaluation surface) of the film portion 2. However, only a part of this region is schematically shown in the drawing.

[0054] Among these weight portions 4, the spring portion 4a, which is the portion on the side attached to the film portion 2, has a height of 3 mm, a dynamic storage modulus at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 MPa or more and 100 MPa or less, and a loss tangent at 23°C in the frequency range of 1 Hz to 1000 Hz of 0.01 or more and 0.50 or less, and is made of an elastic body. More specifically, the spring portion 4a of this embodiment has a dynamic storage modulus (E') of 0.60 MPa and a loss tangent (tanδ) 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 (tanδ) 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 (tanδ) of 0.17 at 23°C and a frequency of 100 Hz, a dynamic storage modulus (E') of 1.31 MPa and a loss tangent (tanδ) 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 on the side opposite to the side attached to the film portion 2, also has a height of 3 mm and is made of rigid stainless steel (SUS304). The mass of the weight portion 4 is approximately 0.8 g, and it has a resonance with a peak in the frequency range of 600 Hz to 650 Hz with respect to the direction perpendicular to the installation surface of the weight portion 4. The overall planar shape of the sound insulation structure portion 1 is a square of 26 cm × 26 cm, the thickness is 12 mm, and the weight is 173.1 g.

[0055] In the sound insulation structure 10 of this embodiment, similar to the configuration shown in FIG. 1, a vibration insulation layer 9 is provided along the support wall portion 3 located on the outermost periphery of the sound insulation structure portion 1. This vibration insulation layer 9 is made of EPDM with the same durometer A hardness of 70 as the film portion 2. The film thickness of this vibration insulation layer 9 is 0.5 mm and the weight is 18.84 g.

[0056] As shown in Fig. 11, the end face of the support wall portion 3 of the sound insulation structure portion 1 of the present embodiment, which is opposite to the end face in contact with the film portion 2, is placed on an iron plate 8 with a thickness of 0.8 mm and a weight of 407.2 g via a vibration insulation layer 9, and the sound insulation property was measured with the surface on the side opposite to the side where the sound insulation structure portion 1 of the iron plate 8 was placed as the incident sound side. Specifically, in accordance with the intensity method shown in JIS A1441-1, a test facility room where the sound source room is a reverberation room and the receiving room is a semi-anechoic room was used, and the acoustic transmission loss (transmission loss) [dB] with respect to the 1 / 3 octave band center frequency [Hz] by 1 / 3 octave band analysis was obtained. The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss was obtained and is shown in Table 1 and Fig. 12(A). The higher the acoustic transmission loss, the higher the sound insulation property. Note that at the 1 / 3 octave band center frequencies [Hz] shown in Figs. 16(A) to 16(C), 1 kHz is 1000 Hz, and the prefix "k" means 1000. The areal density is a value calculated from the weight and area of the sample. The areal density of the configuration including the sound insulation structure 10 and the iron plate 8 of the present embodiment is 8.6 kg / m 2 is.

[0057]

Table 1

[0058] [Example 2] The sound insulation structure portion 1 of the sound insulation structure 10 of Example 2 of the present invention is the same as the sound insulation structure portion 1 of Example 1. In the sound insulation structure 10 of the present embodiment, a vibration insulation layer 9 is provided along the support wall portion 3 located on the outermost periphery of the sound insulation structure portion 1, similar to the configuration shown in Fig. 1. The vibration insulation layer 9 of the present embodiment is a fiber material, specifically, with a density of 0.043 g / cm 3It is made of polypropylene fibers. The film thickness of this vibration insulation layer 9 is 4.5 mm and the weight is 5.7 g. Since the other configurations are the same as those in Example 1, the description thereof is omitted. As shown in Fig. 13, the end face of the support wall portion 3 of the sound insulation structure portion 1 on the side opposite to the side attached to the film portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm and a weight of 407.2 g via the vibration insulation layer 9 to obtain sound insulation performance, which is shown in Table 1 and Fig. 12(B). The areal density of the configuration including the sound insulation structure 10 and the iron plate 8 of this example is 8.6 kg / m 2 is.

[0059] [Example 3] The sound insulation structure portion 1 of the sound insulation structure 10 of Example 3 of the present invention is the same as the sound insulation structure portion 1 of Example 1. In the sound insulation structure 10 of this example, a vibration insulation layer 9 is provided so as to cover the entire sound insulation structure portion 1 in the same configuration as shown in Fig. 4. This vibration insulation layer 9 is made of EPDM having the same durometer A hardness of 70 as the vibration insulation layer 9 of Example 1. The film thickness of this vibration insulation layer 9 is 0.5 mm and the weight is 46.18 g. Since the other configurations are the same as those in Example 1, the description thereof is omitted. As shown in Fig. 14, the end face of the support wall portion 3 of the sound insulation structure portion 1 on the side opposite to the side attached to the film portion 2 is placed on an iron plate 8 having a thickness of 0.8 mm and a weight of 407.2 g via the vibration insulation layer 9 to obtain sound insulation performance, which is shown in Table 1 and Fig. 12(C). The areal density of the configuration including the sound insulation structure 10 and the iron plate 8 of this example is 9.3 kg / m 2 is.

[0060] [Comparative Example 1] As Comparative Example 1, a configuration having the same areal density (8.6 kg / m 2 ) as the sound insulation structures 10 and the iron plate 8 of Examples 1 and 2 is assumed, and the theoretical value of the sound insulation performance of that configuration calculated based on the mass law is obtained, and the relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and Figs. 12(A) and 12(B).

[0061] [Comparative Example 2] As Comparative Example 2, as shown in FIG. 15, a structural portion 12 composed only of a film portion 2 and a support wall portion 3 is placed on an iron plate 8 having a thickness of 0.8 mm and a weight of 407.2 g via a vibration insulation layer 9, and the sound insulation performance is measured. The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and FIG. 12(A). The film portion 2, the support wall portion 3, and the vibration insulation layer 9 of this example are the same as those of Example 1, but the weight portion 4 does not exist. The weight of this structural portion 12 is 140.68 g, and the areal density of the configuration including the structure composed of the structural portion 12 and the vibration insulation layer 9 and the iron plate 8 is 8.1 kg / m 2 is.

[0062] [Comparative Example 3] As Comparative Example 3, as shown in FIG. 16, a rubber plate 13 having a thickness of 3 mm is placed on an iron plate 8 having a thickness of 0.8 mm and a weight of 407.2 g via a vibration insulation layer 9, and the sound insulation performance is measured. The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and FIGS. 12(A) and 12(B). The vibration insulation layer 9 of this example is the same as that of Example 1. The weight of the rubber plate 13 is 170.29 g, and the areal density of the configuration including the structure composed of the rubber plate 13 and the vibration insulation layer 9 and the iron plate 8 is the same as that of Examples 1 and 2 and Comparative Example 1, which is 8.6 kg / m 2 is.

[0063] [Comparative Example 4] As Comparative Example 4, as shown in FIG. 17, a structural portion 12 composed only of a film portion 2 and a support wall portion 3 is placed on an iron plate 8 having a thickness of 0.8 mm and a weight of 407.2 g via a vibration insulation layer 9, and the sound insulation performance is measured. The relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and FIG. 12(B). The film portion 2 and the support wall portion 3 of this example are the same as those of Example 1, and the vibration insulation layer 9 of this example is the same as that of Example 2, but the weight portion 4 does not exist. The weight of this structural portion 12 is 140.68 g, and the areal density of the configuration including the structure composed of the structural portion 12 and the vibration insulation layer 9 and the iron plate 8 is 8.1 kg / m 2 is.

[0064] [Comparative Example 5] As Comparative Example 5, assuming the same surface density (9.3 kg / m 2 ) as that of the sound insulation structure 10 and the iron plate 8 in Example 3, the theoretical value of the sound insulation performance of that configuration calculated based on the mass law was obtained, and the relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and Fig. 12(C).

[0065] [Comparative Example 6] As Comparative Example 6, as shown in Fig. 18, on an iron plate 8 with a thickness of 0.8 mm and a weight of 407.2 g, a structural part 12 composed only of the film part 2 and the support wall part 3 was placed via a vibration insulation layer 9 to measure the sound insulation performance, and the relationship between the 1 / 3 octave band center frequency and the acoustic transmission loss is shown in Table 1 and Fig. 12(C). The film part 2 and the support wall part 3 of this example are the same as those of the film part 2 and the support wall part 3 in Example 1, and the vibration insulation layer 9 of this example is the same as the vibration insulation layer 9 in Example 3, but the weight part 4 does not exist. The weight of this structural part 12 is 140.68 g, and the surface density of the configuration including the structure composed of the structural part 12 and the vibration insulation layer 9 and the iron plate 8 is 8.8 kg / m 2 .

[0066] [Results] The results of comparing Examples 1 to 3 and Comparative Examples 1 to 6 of the present invention described above will be explained. Referring to Figs. 12(A) to 12(C), it can be seen that the sound insulation effect is improved by the sound insulation structure part 1 of the sound insulation structure 10 of the present invention. In particular, according to the sound insulation structure parts 1 of Examples 1 to 3, in a frequency band higher than 630 Hz, a significantly greater sound insulation effect than the theoretical value (Comparative Examples 1, 5) based on the mass law is obtained, indicating that the effect of the present invention is significant. And in particular, when compared with Comparative Examples 2, 4, and 6 in a frequency band lower than 1.25 kHz, it can be seen that the sound insulation performance of Examples 1 to 3 having the weight part 4 is high. Also, when comparing Examples 1 to 3 with Comparative Example 3, it can be seen that the sound insulation structure 10 of the present invention exhibits excellent sound insulation performance compared to the configuration having a rubber plate 13 which is an example of a conventional general sound insulation material. And when comparing Examples 1 to 3, it can be seen that even if the materials and shapes of the vibration insulation layers 9 are different, as long as each is within a preferable range of materials and shapes, high sound insulation performance is exhibited. Therefore, it can be seen that the materials and shapes of the vibration insulation layer 9 can be freely set within a preferable range.

[0067] The present invention may have the following configuration. [1] A sound insulation structure including a sound insulation structure portion and a vibration insulation layer, wherein the sound insulation structure portion has an elastic film portion, a support wall portion standing on the film portion and having elasticity, and a weight portion standing on the film portion, the film portion is divided into a plurality of compartments by the support wall portion, and the weight portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartments where the weight portions are located, one weight portion is arranged in one compartment, the height of the support wall portion extending in a direction perpendicular to the film portion is greater than the height of the weight portion extending in a direction perpendicular to the film 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, the vibration insulation layer is arranged between the entire surface or a part of the support wall portion of the sound insulation structure portion and the end surface on the opposite side of the end surface in contact with the film portion, and the installation surface on which the sound insulation structure is installed. The sound insulation structure is characterized by this. [2] The sound insulation structure according to [1], wherein any one of the film portion, the support wall portion, and the spring portion is made of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, or a material having both rubber elasticity and energy elasticity. [3] The sound insulation structure according to [1] or [2], wherein any one of the film portion, the support wall portion, and the spring portion has a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C. [4] The sound insulation structure according to any one of [1] to [3], wherein any one of the film portion, the support wall portion, and the spring portion has a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C. [5] The spring portion of the hammer portion is located on the side attached to the film portion of the hammer portion, and the mass portion is located on the side opposite to the side attached to the film portion of the hammer portion. The sound insulation structure according to any one of [1] to [4]. [6] The mass portion of the hammer portion has a larger volume than the spring portion. The sound insulation structure according to any one of [1] to [5]. [7] The mass portion of the hammer portion is made of a material having a higher density than the spring portion. The sound insulation structure according to any one of [1] to [6]. [8] A sound insulation structure including a sound insulation structure portion and a vibration insulation layer, The sound insulation structure portion has an elastic film portion, a support wall portion that stands on the film portion and has elasticity, and a hammer portion that stands on the film portion. The film portion is divided into a plurality of compartments by the support wall portion, and the hammer portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartment where the hammer portion is located inside, one hammer portion is arranged in one compartment. The height of the support wall portion extending in the direction perpendicular to the film portion is larger than the height of the hammer portion extending in the direction perpendicular to the film portion. The film portion serves as a spring portion, and the hammer portion serves as a mass portion to constitute a spring-mass resonator. The vibration insulation layer is arranged between the entire surface or a part of the support wall portion of the sound insulation structure portion and the end surface opposite to the end surface in contact with the film portion, and the installation surface on which the sound insulation structure is installed. The sound insulation structure characterized by this. [9] Both the film portion and the support wall portion are made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. The sound insulation structure according to [8].

[10] Both the film portion and the support wall portion have a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C. The sound insulation structure according to [8] or [9].

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

[10] , wherein both the film portion and the support wall portion 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.

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

[11] , wherein the vibration insulation layer is disposed between an end surface of the support wall portion located at the outermost periphery of the sound insulation structure portion, which is opposite to the end surface in contact with the film portion, and the installation surface.

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

[12] , wherein the vibration insulation layer is disposed between the entire sound insulation structure portion and the installation surface.

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

[13] , wherein the vibration insulation layer is made of a resin material or a porous material having rubber elasticity.

[15] The sound insulation structure according to

[14] , wherein the vibration insulation layer is made of a resin material having a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and 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.

[16] The vibration insulation layer has a density of 0.001 g / cm 3 or more 3 and 0.5 g / cm or less, and is the sound insulation structure according to

[14] .

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

[16] , wherein the thickness of the vibration insulation layer is 0.5 mm or more and 10 mm or less.

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

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

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

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

[20] The area of each of the compartments is 100 mm 2 or more and 1000 mm 2The sound insulation structure according to any one of [1] to

[19] below.

[21] 10 or more and 1000 or less of the said compartments are provided per 1000 cm of the area of the said film part. 2 The sound insulation structure according to any one of [1] to

[20] , wherein 10 or more and 1000 or less of the said compartments are provided per 1000 cm of the area of the said film part.

[22] 50 or more and 500 or less of the said compartments are provided per 1000 cm of the area of the said film part. 2 The sound insulation structure according to

[21] , wherein 50 or more and 500 or less of the said compartments are provided per 1000 cm of the area of the said film part.

[23] The plate thickness of the said support wall part is 0.5 mm or more and 5.0 mm or less. The sound insulation structure according to any one of [1] to

[22] .

[24] The plate thickness of the said support wall part is 1.0 mm or more and 3.0 mm or less. The sound insulation structure according to

[23] .

[25] The film thickness of the said film part is 0.1 mm or more and 3.0 mm or less. The sound insulation structure according to any one of [1] to

[24] .

[26] The height in the direction perpendicular to the said film part is 5 mm or more and 20 mm or less. The sound insulation structure according to any one of [1] to

[25] .

[27] The height of the said support wall part extending in the direction perpendicular to the said film part is 5 mm or more and 20 mm or less. The sound insulation structure according to any one of [1] to

[26] .

[28] The height of the said weight part extending in the direction perpendicular to the said film part is 1 mm or more. The sound insulation structure according to any one of [1] to

[27] .

[29] The durometer A hardness of the said film part is 50 or more, and the durometer A hardness of the said support wall part is 1 or more and 90 or less. The sound insulation structure according to any one of [1] to

[28] .

Explanation of Signs

[0068] 1, 6 Sound insulation structure part 2 Film part 3 Support wall part 3a First wall part 3b Second wall part 4, 7 Weight part 4a Spring part 4b Mass part 5 Compartment (unit structure) 8 Iron plate 9 Vibration isolation layer 10 Sound insulation structure 11 Installation surface 12 Structural part 13 Rubber plate

Claims

1. A sound insulation structure including a sound insulation structure portion and a vibration insulation layer, wherein the sound insulation structure portion has an elastic film portion, a support wall portion standing on the film portion and having elasticity, and a weight portion standing on the film portion, the film portion is divided into a plurality of compartments by the support wall portion, and the weight portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartments where the weight portions are located, one weight portion is arranged in one compartment, the height of the support wall portion extending in a direction perpendicular to the film portion is greater than the height of the weight portion extending in a direction perpendicular to the film portion, each of the weight portions constitutes a spring mass resonator having an elastic spring portion and a mass portion having a greater mass than the spring portion, the vibration insulation layer is arranged between the end surface on the opposite side of the end surface in contact with the film portion of the entire surface or a part of the support wall portion of the sound insulation structure portion and the installation surface on which the sound insulation structure is installed. A sound insulation structure characterized by that.

2. The sound insulation structure according to claim 1, wherein each of the film portion, the support wall portion, and the spring portion is made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity.

3. The sound insulation structure according to claim 1 or 2, wherein each of the film portion, the support wall portion, and the spring portion has a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C.

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

5. The sound insulation structure according to claim 1 or 2, wherein the spring portion of the weight portion is located on the side attached to the film portion of the weight portion, and the mass portion is located on the side opposite to the side attached to the film portion of the weight portion.

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

7. The sound insulation structure according to claim 1 or 2, wherein the mass portion of the weight portion is made of a material having a higher density than the spring portion.

8. A sound insulation structure including a sound insulation structure portion and a vibration insulation layer, The sound insulation structure portion has an elastic film portion, a support wall portion that stands on the film portion and has elasticity, and a weight portion that stands on the film portion. The film portion is divided into a plurality of compartments by the support wall portion, and the weight portions are respectively located inside all of the plurality of compartments or inside some of the plurality of compartments. In the compartments where the weight portions are located, one weight portion is arranged in one compartment. The height of the support wall portion extending in the direction perpendicular to the film portion is greater than the height of the weight portion extending in the direction perpendicular to the film portion. The film portion serves as a spring portion, and the weight portion serves as a mass portion to constitute a spring-mass resonator. The vibration isolation layer is disposed between the end surface on the opposite side of the end surface in contact with the film portion of the entire surface or a part of the support wall portion of the sound insulation structure portion and the installation surface on which the sound insulation structure is installed. A sound insulation structure characterized by this.

9. Both the film portion and the support wall portion are made of any one of a material having no energy elasticity but having rubber elasticity, a material having no rubber elasticity but having energy elasticity, and a material having both rubber elasticity and energy elasticity. The sound insulation structure according to claim 8.

10. Both the film portion and the support wall portion have a dynamic storage elastic modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C. The sound insulation structure according to claim 8 or 9.

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

12. The vibration isolation layer is disposed between the end surface on the opposite side of the end surface in contact with the film portion of the support wall portion located on the outermost periphery of the sound insulation structure portion and the installation surface. The sound insulation structure according to claim 1 or 8.

13. The vibration isolation layer is disposed between the entire sound insulation structure portion and the installation surface. The sound insulation structure according to claim 1 or 8.

14. The vibration isolation layer is made of a resin material having rubber elasticity or a porous material. The sound insulation structure according to claim 1 or 8.

15. The vibration insulating layer is made of a resin material having a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at a frequency of 1 Hz to 1000 Hz at 23°C and a loss tangent of 0.01 or more and 0.50 or less at a frequency of 1 Hz to 1000 Hz at 23°C, and the sound insulation structure according to claim 14.

16. The vibration insulating layer is made of a porous material having a density of 0.001 g / cm 3 or more and 0.5 g / cm 3 or less, and the sound insulation structure according to claim 14.

17. The thickness of the vibration insulating layer is 0.5 mm or more and 10 mm or less, and the sound insulation structure according to claim 1 or 8.

Images