Soundproof structure

Abstract

To provide a thin and light-weight soundproof structure that has sufficient sound insulation performance and easy installability onto a curved installation surface, and is difficult to dent even if pressed.SOLUTION: A soundproof structure 10 has a base part 8, a product part 9 and a sound insulation structure 1 therebetween. The sound insulation structure 1 has a film part 2 having elasticity, support wall parts 3 vertically installed on the film part 2 and having elasticity, and weight parts 4 vertically installed on the film part 2. The film part 2 is divided into plural sections 5 by the support wall parts 3, the weight part 4 is positioned in one or all of the plural sections 5, and one weight part 4 is placed in one section 5. A height H1 of the support wall part 3 is higher than a height H2 of the weight part 4. Each of the weight parts 4 configures a spring mass resonator having a spring part 4a having elasticity and a mass part 4b having larger mass than the spring part 4a. The film part 2 faces one of the product part 9 and the base part 8, and an end of the support wall part 3 on the opposite side against the film part 2 faces the other of the product part 9 and the base part 8.SELECTED DRAWING: Figure 1

Description

[Technical field]

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

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

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

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

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

[0006] The vibration reduction device of the invention described in Patent Document 4 has an acoustic meta-structure that is attached to the vehicle body and blocks vibrations transmitted through the vehicle body, and includes a cross-shaped frame that is attached to the vehicle body and divides a certain space into certain areas, and vibrators that are configured at the corners of each area divided by the frame and have their own natural frequencies, blocking vibrations transmitted from the vehicle body through the frame.

[0007] The sound insulation structure described in Patent Document 5 has a resonating portion having multiple convex rubber elasticity and a sheet-like support body that supports the resonating portion, the resonating portion having a storage modulus G' of 100 MPa or less at 25°C and 10 kHz, and the support body having an areal density of 1.0 kg / m 2 The following is the result.

[0008] In the double wall described in Patent Document 6, a single-layer or multi-layer plate material is attached to one side of a support material consisting of at least one pair of pillars and studs, and on the other side of the support material, a single-layer or multi-layer plate material preferably having a metal plate is fixed to the pair of pillars and attached so as not to come into contact with the studs, and a bulk density of 10 kg / m is provided between the two plates. 3 ~48kg / m 3 A fibrous porous material is interposed. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] JP 2005-250474 A [Patent Document 2] International Publication No. 2019 / 022245 [Patent Document 3] JP 2021-152584 A [Patent Document 4] JP 2020-91481 A [Patent Document 5] International Publication No. 2019 / 208727 [Patent Document 6] JP 2002-004467 A Summary of the Invention [Problem to be solved by the invention]

[0010] The sound-damping panel described in Patent Document 1 has a rigid frame that is not flexible, and vibrations are transmitted to the seat via this rigid frame, so there is a risk that sufficient sound insulation cannot be obtained. In addition, if the support surface on which the rigid frame is placed is curved or uneven, the sound-damping panel may not be stably held. In particular, since the panels of general vehicles (e.g., automobiles) often have curved support surfaces or uneven parts, it is difficult to simply use the sound-damping panel of Patent Document 1 as a sound-insulating material for vehicles. In addition, the rigid frame has a large mass, and the increase in mass due to the sound-insulating material in the vehicle may be a problem.

[0011] The soundproofing material described in Patent Document 2 has a high support part, i.e., a high height extending from the seat in a direction perpendicular to the seat, and is preferably 25 mm or more. In order to stably support the seat with such a high support part, it is preferable that the support part has rigidity. As a result, there is a risk that sufficient sound insulation cannot be obtained because vibrations are transmitted through the support part, and it is difficult to place the soundproofing material on a curved or uneven support surface such as a panel of a vehicle (e.g., an automobile). In addition, such a high support part leads to an increase in size and weight of the entire soundproofing material, and when placed on a panel of a vehicle, the soundproofing material occupies a large space inside the vehicle, reducing space efficiency, and there is a concern that it will hinder the installation of other components and get in the way of occupants.

[0012] In the sound insulation material described in Patent Document 3, the resonating part, which is the functional part that exerts the sound insulation effect, is exposed and not covered by a supporting wall, etc., and there is a risk that the sound insulation performance will decrease or change if this resonating part comes into contact with other members or the human body. Therefore, it is necessary to provide a large space around the resonating part, which reduces the space efficiency.

[0013] The vibration reduction device described in Patent Document 4 does not have a membrane part, but is composed of a plurality of vibrators and a frame connecting them. Therefore, like the sound insulation material of Patent Document 3, the vibrator, which is a functional part that exerts a sound insulation effect, is exposed, and if this vibrator comes into contact with other members or the human body, the sound insulation may be reduced or changed. In addition, in order to ensure the minimum structural strength of the vibration reduction device, the frame is required to have rigidity. As a result, since vibration is transmitted through the frame, there is a risk that sufficient sound insulation cannot be obtained, and it is difficult to place the vibration reduction device of Patent Document 4 on a curved mounting surface or a mounting surface having unevenness, such as a panel of a vehicle (e.g., an automobile).

[0014] In the sound insulation structure described in Patent Document 5, a rib-shaped protrusion higher than the resonating parts is provided near the outer periphery of the sheet-like support and outside the area where many resonating parts are formed. However, no rib-shaped protrusion is provided in the large-area resonating part forming area. Therefore, when the resonating part forming area, which is the central part of the sheet-like support, is pressed from the opposite side to the resonating parts, it is easily dented because it is not supported by the rib-shaped protrusion. In addition, when the end face of the rib-shaped protrusion opposite to the support is placed on and held on various members (e.g., a vehicle panel), the installation stability of this sound insulation structure is poor because the resonating part forming area between the rib-shaped protrusion and the opposing rib-shaped protrusion is wide.

[0015] The double wall described in Patent Document 6 requires a fibrous porous material between two plates, which makes the manufacturing process complicated. In addition, the soundproofing effect is limited to a low frequency range of 100 Hz or less.

[0016] Therefore, the object of the present invention is to provide a soundproofing structure that has sufficient sound insulation, can be easily and stably placed on curved or uneven surfaces such as the panels of buildings, machinery, and vehicles (e.g., automobiles), is not easily dented when pressed, and can be made thin and lightweight, and has particularly good soundproofing effects in the frequency range of 1000 Hz or less. [Means for solving the problem]

[0017] The soundproof structure of the present invention comprises a base, a product portion, and a sound-insulating structure located between the base and the product portion, the sound-insulating structure comprising an elastic film portion, an elastic support wall portion erected on the film portion, and a weight portion erected on the film portion, the film portion being divided into a plurality of compartments by the support wall portion, the weight portions being located within all of the plurality of compartments or within some of the plurality of compartments, and in the compartments within which the weight portions are located, One weight portion is arranged in one of the compartments, the height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than the height of the weight portion extending in a direction perpendicular to the membrane portion, each of the weight portions constitutes a spring mass resonator having an elastic spring portion and a mass portion having a greater mass than the spring portion, the membrane portion faces one of the product portion and the base portion, and the end face of the support wall portion opposite the membrane portion faces the other of the product portion and the base portion. The term "elasticity" used here refers to the property of a solid substance that has been deformed by an external force returning to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, a substance is said to have "elasticity" when it has at least one of energy elasticity and rubber elasticity (entropy elasticity). The membrane portion, the support wall portion and the spring portion may all be made of a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity. The film portion, the supporting wall portion, and the spring portion may all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. The film portion, the supporting wall portion, and the spring portion may all be made of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. Specifically, the elasticity of the film part, the supporting wall part, and the spring part is evaluated by a dynamic storage modulus (E') obtained by measuring frequency dependency in tension or compression mode with a dynamic viscoelasticity measuring device in accordance with JIS K7244 and obtaining a master curve based on 23° C., and the dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz is 0.01 MPa or more and 100 MPa or less. More preferably, both the film part and the supporting wall part may be made of an elastic body having a dynamic storage modulus (E') at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 MPa or more and 50 MPa or less, and a loss tangent at 23° C. and at a frequency of 1 Hz to 1000 Hz of 0.05 or more and 0.45 or less. The spring portion of the weight may be located on a side of the weight that is attached to the membrane portion, and the mass portion may be located on a side of the weight that is opposite to the side that is attached to the membrane portion. The mass portion of the weight portion may have a larger volume than the spring portion. The mass portion of the weight portion may be made of a material having a higher density than the spring portion.

[0018] Another soundproof structure of the present invention comprises a base, a product portion, and a sound-proofing structure located between the base and the product portion, the sound-proofing structure comprising an elastic membrane portion, an elastic supporting wall portion erected on the membrane portion, and a weight portion erected on the membrane portion, the membrane portion is divided into a plurality of compartments by the supporting wall portion, the weight portion is located inside all of the plurality of compartments or inside some of the plurality of compartments, and in the compartment in which the weight portion is located, one weight portion is disposed in one of the compartments, the height of the supporting wall portion extending in a direction perpendicular to the membrane portion is greater than the height of the weight portion extending in a direction perpendicular to the membrane portion, the membrane portion serves as a spring portion and the weight portion serves as a mass portion to constitute a spring-mass resonator, the membrane portion faces one of the product portion and the base, and the end face of the supporting wall portion opposite the membrane portion faces the other of the product portion and the base. Both the membrane portion and the supporting wall portion may be made of any of a material that has rubber elasticity but not energy elasticity, a material that has energy elasticity but not rubber elasticity, or a material that has both rubber elasticity and energy elasticity. Both the film part and the supporting wall part may have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. Also, both the film part and the supporting wall part may be made of an elastic body having a loss tangent of 0.01 or more and 0.50 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz. More preferably, both the film part and the supporting wall part may be made of an elastic body having a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23° C. and at a frequency of 1 Hz to 1000 Hz, and a loss tangent of 0.05 or more and 0.45 or less at 23° C. and at a frequency of 1 Hz to 1000 Hz.

[0019] The soundproof structure of the present invention and another soundproof structure may have the following configuration. The thickness of the base may be 0.01 mm or more and 10 mm or less. The membrane portion may be adhered to the product portion by an adhesive film, and an end face of the support wall portion opposite the membrane portion may face the base portion in a contacting or non-contacting state. The base may be a panel of a vehicle and the product portion may be a portion of a product located within the interior of the vehicle. The support wall portion may include a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending in a first direction parallel to the membrane portion, and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and extending in a second direction perpendicular to the first direction. The support wall portion may be cylindrical having a circular, elliptical or oval cross-sectional shape that defines each of the compartments, or may be rectangular tubular having a polygonal cross-sectional shape that defines each of the compartments, specifically a square, regular pentagon or regular hexagon. The area of ​​each of the compartments is 100 mm 2 More than 1000mm 2 It may be the following: The area of ​​the membrane is 1000 cm 2 There may be from 10 to 1000 such compartments per unit area, and more preferably from 50 to 500 such compartments per unit area. The plate thickness of the support wall portion may be 0.5 mm or more and 5.0 mm or less, and is more preferably 1.0 mm or more and 3.0 mm or less. The film thickness of the film portion may be 0.1 mm or more and 3.0 mm or less. The height in a direction perpendicular to the film portion may be 5 mm or more and 20 mm or less. The height of the support wall in the direction perpendicular to the membrane may be 5 mm to 20 mm, and more preferably 10 mm to 20 mm. The support wall may have different heights in parts. The weight portion may have a height of 1 mm or more extending in a direction perpendicular to the film portion. The film portion may have a durometer A hardness of 50 or more, and the support wall portion may have a durometer A hardness of 1 or more and 90 or less. The durometer A hardness can be obtained by measurement in accordance with JIS K 6253-3. Effect of the Invention

[0020] According to the present invention, a soundproofing structure can be provided which has sufficient sound insulation, can be easily and stably placed on curved or uneven surfaces such as the panels of buildings, machinery, and vehicles (e.g., automobiles), is not easily dented when pressed, and can be made thin and lightweight, and which has particularly good soundproofing effects in the frequency range of 1000 Hz or less. [Brief description of the drawings]

[0021] [Figure 1] 1 is a cross-sectional view of a soundproof structure according to a first embodiment of the present invention. [Diagram 2] 2A is a perspective view of the soundproofing structure of the soundproofing structure shown in FIG. 1, and FIG. 2B is a cross-sectional view taken along line AA of FIG. [Diagram 3] 3(A) is an exploded perspective view of one section of the sound-proofing structure shown in FIG. 2, and (B) is an exploded front view thereof. [Figure 4] FIG. 1A is a perspective view of a soundproofing structure of a modified example of the first embodiment of the present invention, and FIG. 1B is a cross-sectional view of the soundproofing structure taken along line AA. [Diagram 5] FIG. 1A is a cross-sectional view of a soundproofing structure according to another modified example of the first embodiment of the present invention, and FIG. 1B is a perspective view of a weight portion of a sound-insulating structure of the soundproofing structure. [Figure 6] FIG. 1A is a cross-sectional view of a soundproofing structure according to still another modified example of the first embodiment of the present invention, and FIG. 1B is a perspective view of a weight portion of a sound-insulating structure of the soundproofing structure. [Figure 7] FIG. 10A is a perspective view of a soundproofing structure of a soundproofing structure according to a second embodiment of the present invention, and FIG. 10B is a cross-sectional view of the soundproofing structure taken along line AA. [Figure 8] FIG. 13(A) is a cross-sectional view of a soundproofing structure according to a modified example of the second embodiment of the present invention, and (B) is a perspective view of a weight portion of a sound-insulating structure of the soundproofing structure. [Figure 9] FIG. 1A is a plan view showing a schematic diagram of one section of a soundproofing structure of the present invention, and FIG. 1B is a plan view showing a schematic diagram of a plurality of sections. [Figure 10] FIG. 2(A) is a plan view showing a schematic diagram of one section of another example of a soundproofing structure of the present invention, and FIG. 2(B) is a plan view showing a schematic diagram of a plurality of sections. [Figure 11] FIG. 1(A) is a plan view showing a schematic diagram of one section of a further example of a soundproofing structure of the present invention, and FIG. 1(B) is a plan view showing a schematic diagram of a plurality of sections. [Figure 12] FIG. 1(A) is a plan view showing a schematic diagram of one section of a further example of a soundproofing structure of the present invention, and FIG. 1(B) is a plan view showing a schematic diagram of a plurality of sections. [Figure 13] FIG. 1(A) is a plan view showing a schematic diagram of one section of a further example of a soundproofing structure of the present invention, and FIG. 1(B) is a plan view showing a schematic diagram of a plurality of sections. [Figure 14] FIG. 1A is a side view showing a schematic diagram of an automobile in which a soundproofing structure of the present invention is installed, and FIGS. 1B to 1E are perspective views showing the state in which the soundproofing structure is installed in the automobile. [Figure 15] 1 is a cross-sectional view showing a soundproof structure according to a first embodiment of the present invention. [Figure 16] Graph (A) is a graph showing the sound insulation properties of Example 1 of the present invention and Comparative Examples 1 to 3, and graph (B) is a graph showing the sound insulation properties of Examples 1 and 2 of the present invention and Comparative Example 1. [Figure 17] Graph (A) is a graph showing the sound insulation properties of Examples 1, 3, and 4 of the present invention and Comparative Example 1, and graph (B) is a graph showing the sound insulation properties of Example 1 of the present invention and Comparative Examples 1 and 4. [Figure 18] FIG. 1 is a cross-sectional view showing a schematic method for evaluating the susceptibility of a soundproof structure to dents. [Figure 19] FIG. 4 is a cross-sectional view showing the soundproof structure of Comparative Example 2. [Figure 20] FIG. 11 is a cross-sectional view of the structure of Comparative Example 3. [Figure 21] FIG. 11 is a cross-sectional view of the structure of Comparative Example 4. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. [First embodiment] FIG. 1 is a cross-sectional view of a soundproof structure 10 according to a first embodiment of the present invention. This soundproof structure 10 has a structure in which a soundproofing structure 1 is sandwiched between a base 8 and a product part 9. Both the base 8 and the product part 9 are parts of a vehicle, equipment, etc. that require soundproofing, the base 8 is a panel (e.g., a dash panel of an automobile) that constitutes a part of the body of the vehicle, equipment, etc. (e.g., an automobile), and the product part 9 is a part of a part (e.g., a trim part of an automobile) that is attached to the inside or outside of the vehicle or equipment. The soundproofing structure 1 may be held in a state in which it abuts against both the base 8 and the product part 9, or may be held in a state in which it abuts against only one of the base 8 and the product part 9. Furthermore, the soundproofing structure 1 may be held by some means (not shown) in a state in which it abuts against neither the base 8 nor the product part 9.

[0023] FIG. 2(A) is a perspective view of a sound insulation structure 1 of a sound insulation structure 10 of this embodiment, and FIG. 2(B) is a cross-sectional view of the sound insulation structure 10 of this embodiment cut along line AA in FIG. 2(A) and turned upside down. The sound insulation structure 1 has an elastic sheet-like film portion 2, an elastic support wall portion 3 standing substantially vertically from the film portion 2, and a weight portion 4 standing substantially vertically from the film portion 2. The film portion 2 is divided into a plurality of sections (unit structures) 5 by the support wall portion 3. The weight portion 4 is located in each of the plurality of sections 5, or in some of the plurality of sections 5. In the section 5 in which the weight portion 4 is located, one weight portion 4 is located in one section 5. FIG. 3(A) is an exploded perspective view of one section 5 of the sound insulation structure 1, and FIG. 3(B) is an exploded front view thereof. The height H1 of the support wall 3 extending from the membrane 2 in a direction perpendicular to the membrane 2 is greater than the height H2 of the weight 4 extending from the membrane 2 in a direction perpendicular to the membrane 2. Each weight 4 constitutes a spring mass resonator having an elastic spring 4a and a mass 4b having a larger mass than the spring 4a. The term "elasticity" as used here refers to the property of a solid material that has been deformed by an external force and returns to its original shape when the external force is removed, and includes energy elasticity and rubber elasticity (entropy elasticity). Here, the term "having elasticity" refers to the case where at least one of energy elasticity and rubber elasticity (entropy elasticity) is present.

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

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

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

[0027] The section 5 of the sound insulation structure 1 of this embodiment has a membrane part 2 with an area of ​​1000 cm 2 It is preferable to provide 10 to 1000 sections per unit area, and more preferable to provide 50 to 500 sections per unit area. This prevents the number of sections 5 from being too small, and achieves the effect of dividing the entire sound insulation structure 1 into a plurality of sections 5 so that each section can exhibit a sufficient sound insulation effect, thereby preventing a decrease in the sound insulation performance of the entire sound insulation structure 1. In addition, the number of sections 5 is not too large, and the weight of the entire sound insulation structure 1 can be reduced. The planar area of ​​each section 5 is 100 mm 2 More than 1000mm 2 It is preferable that the length is less than 200 mm. 2 More than 800mm 2 It is more preferable that the height of the entire sound insulation structure 1 in the direction perpendicular to the film portion 2 is 5 mm or more and 20 mm or less. As a result, the area of ​​the planar shape of each of the sections 5 is not too small, making it easy to arrange the weight portion 4 inside, and the area is not too large, so that sufficient sound insulation can be maintained by the effect of the weight portion 4 on the film portion 2. It is preferable that the height of the entire sound insulation structure 1 in the direction perpendicular to the film portion 2 is 5 mm or more and 20 mm or less. As a result, the height of the entire sound insulation structure 1 is not too low, so that the weight portion 4 has a sufficient height as a spring mass resonator, and is not too high, so that the entire sound insulation structure 1 can be made lighter. Note that each drawing shows each section 5 and the support wall portion 3, etc., in a schematic manner, and the number and area of ​​the sections 5 and the height of the sound insulation structure 1 may not be shown strictly and accurately, or may not be unified in each drawing, but it is preferable that the number and area of ​​the sections 5 and the height of the sound insulation structure 1 are appropriately designed to be within the above-mentioned numerical ranges.

[0028] The film portion 2, the supporting wall portion 3, and the spring portion 4a of the sound insulation structure 1 of this embodiment are all made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa to 100 MPa at 23° C. and a loss tangent (tan δ) of 0.01 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, preferably a dynamic storage modulus (E') of 0.05 MPa to 50 MPa at 23° C. and a loss tangent (tan δ) of 0.05 to 0.50 at 23° C. and a frequency of 1 Hz to 1000 Hz, respectively. The dynamic storage modulus (E') and the loss tangent (tan δ) are determined by creating a master curve based on 23° C. using a dynamic viscoelasticity tester. By having a dynamic storage modulus (E') of 0.01 MPa or more at 23°C and frequencies of 1 Hz to 1000 Hz, it is possible to prevent deterioration of sound insulation in the target frequency band, and also to prevent deterioration of the shape retention of the film part 2 and the supporting wall part 3. By having a dynamic storage modulus (E') of 100 MPa or less at 23°C and frequencies of 1 Hz to 1000 Hz, it is possible to prevent deterioration of vibration in the frequency band to be sound-insulated, and to prevent the sound-insulating structure 1 from becoming rigid and deteriorating in installation. The film part 2 and the supporting wall part 3 may be formed of the same material or different materials. It is preferable that the film part 2 is also made of a flexible material, that is, any one of a material that does not have energy elasticity but has rubber elasticity, a material that does not have rubber elasticity but has energy elasticity, and a material that has both rubber elasticity and energy elasticity.

[0029] The film portion 2 is preferably a hard elastic film since the weight portion 4 is attached to it. The dynamic storage elastic modulus (E') of the film portion 2 is preferably 15 MPa or more, and the thickness (film thickness) is preferably 0.001 mm or more and 1 mm or less. When the thickness of the film portion 2 is 0.001 mm or more, the film portion 2 is thick and easy to handle, and the film portion 2 is less likely to be damaged during transportation such as shipping. On the other hand, when the thickness of the film portion 2 is 1 mm or less, the thickness and weight of the entire sound insulation structure 1 do not increase, so that the entire sound insulation structure 1 can be prevented from becoming hard and the installation property from being deteriorated. The thickness of the film portion 2 is preferably smaller than the thickness of the product portion 9 described later. The material of the film portion 2 preferably has a durometer A hardness of 30 or more according to JIS K6253, and more preferably 70 or more. When the durometer A hardness of the film portion 2 is 30 or more, the vibration of the film portion 2 is not deteriorated, and the sound insulation property of the frequency band to be sound-insulated is good. The stiffness (axial stiffness) k of the membrane 2 is expressed as k = E' × A / L from the dynamic storage modulus E', the cross-sectional area A of the membrane 2, and the thickness L of the membrane 2. When the area of ​​the membrane 2 to be evaluated for stiffness is 1000 cm 2 When the stiffness k is 10 6 N / mm or more 10 9 N / mm or less is preferable, and 3×10 6 N / mm or more 10 8 It is more preferable that the surface area of ​​the membrane portion 2 is 1000 cm 2 When the stiffness is 10 6 When the surface area of ​​the film 2 is 1000 cm or more, the vibration of the film 2 is not deteriorated, and the sound insulation property of the frequency band to be insulated is good. 2 When the stiffness is 10 9 If the elastic modulus is less than N / mm, the sound insulation structure 1 will not become too rigid, and the installation will not become difficult. The bending rigidity K of the film 2 is expressed as K=E'×I from the dynamic storage modulus E' and the second moment of area I, and the second moment of area I is expressed as I=b×h from the thickness h of the film 2 and the width b of the film 2. 3 / 12. When the area of ​​the membrane part 2 to be evaluated is 1000 cm 2 When the bending stiffness K is 30N / mm 2 Over 10 5 N / mm 2It is preferable that the resistance is less than 50N / mm 2 5×10 or more 4 N / mm 2 It is more preferable that the area of ​​the membrane portion 2 is 1000 cm or less. 2 The bending stiffness K when 2 When the area of ​​the film portion 2 is 1000 cm or more, the deterioration of the vibration of the film portion 2 can be prevented, and the sound insulation property of the target frequency band can be improved. 2 When the bending stiffness K is 10 5 N / mm 2 By satisfying the following, it is possible to prevent the sound insulation structure 1 from becoming too rigid and the installation property from being deteriorated. The cross-sectional shape of the film portion 2 is not particularly limited, and it may be flat or may have irregularities.

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

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

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

[0033] The supporting wall 3 is preferably made of a soft, flexible material within a range capable of supporting the film 2. The plate thickness of the supporting wall 3 is preferably 0.5 mm or more and 5.0 mm or less, and more preferably 1.0 mm or more and 3.0 mm or less. When the plate thickness of the supporting wall 3 is 0.5 mm or more, the shape retention of the sound insulation structure 1 can be maintained. When the plate thickness of the supporting wall 3 is 5.0 mm or less, the vibration of the film 2 is suppressed from deteriorating, the sound insulation of the frequency band to be sound-insulated is improved, and the entire sound insulation structure 1 can be made lighter. The height of the supporting wall 3 extending in a direction perpendicular to the film 2 is preferably 5 mm or more and 20 mm or less, and more preferably 10 mm or more and 20 mm or less. The supporting wall 3 may have a different height in parts. When the height of the supporting wall 3 is different in parts, the higher part may be 10 mm or more and 20 mm or less, more preferably 12 mm or more and 20 mm or less, and even more preferably 14 mm or more and 20 mm or less. The support wall 3 is not too low in height, so that the weight 4 can have a sufficient height as a spring mass resonator. The support wall 3 is not too high in height, so that the weight of the entire structure can be reduced. The material of the support wall 3 preferably has a durometer A hardness according to JIS K6253 of 1 or more and 90 or less, more preferably 10 or more and 70 or less. When the support wall 3 has a durometer A hardness of 1 or more, the shape retention of the sound insulation structure 1 can be maintained. When the support wall 3 has a durometer A hardness of 90 or less, when the support wall 3 comes into contact with the base 8 and vibration is transmitted, the vibration from the support wall 3 is transmitted to the membrane 2, and the sound insulation performance is prevented from being deteriorated, and the sound insulation structure 1 is prevented from becoming rigid and the installation property is prevented from being deteriorated. The stiffness k of the support wall 3 is expressed as k=E'×A / L, where E' is the dynamic storage elastic modulus, A is the cross-sectional area of ​​the support wall 3, and L is the height of the support wall 3. The area of ​​the support wall 3 to be evaluated for rigidity is 1000 cm 2 When the stiffness k is 10N / mm or more, 6 It is preferable that the resistance is less than 10 N / mm. 2 N / mm or more 10 5 It is more preferable that the surface area of ​​the support wall 3 is 1000 cm or less. 2When the area of ​​the support wall 3 is 1000 cm, the stiffness k is 10 N / mm or more, so that the shape retention of the sound insulation structure 1 is good. 2 When the stiffness k is 10 6 By having the resistance be N / mm or less, when the supporting wall portion 3 comes into contact with the base portion 8 and vibration is transmitted thereto, it is possible to prevent the vibration from the supporting wall portion 3 being transmitted to the membrane portion 2, which would deteriorate the sound-proofing performance and also prevent the sound-proofing structure 1 from becoming rigid and making it difficult to install.

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

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

[0036] The material of the mass portion 4b is not particularly limited, but it is made of resin, metal, or the like, and the mass portion 4b has a larger mass than the spring portion 4a, for example, a mass of 0.1 g or more and 2.0 g or less. The mass portion 4b preferably has a mass at least twice the mass of the spring portion 4a. When the weight of the mass portion 4b is 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 there is no risk of deterioration of sound insulation. When the material of the mass portion 4b is resin, the resin may be made of a biomass material.

[0037] The spring constant (rigidity) of the spring portion 4a is determined based on the mass of the mass portion 4b so that the resonant frequency coincides with the frequency to be mainly sound-insulated. As an example, when the mass portion 4b has a mass of 1.0 g and the frequency to be mainly sound-insulated is 1000 Hz or less, the spring constant of the spring portion 4a is 1 N / mm or more and 50 N / mm or less.

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

[0039] In the soundproof structure 10 of this embodiment, the sound insulation structure 1 having the above-described configuration is sandwiched between the base 8 and the product portion 9 in a direction perpendicular to the film portion 2. In the example shown in FIG. 1, the film portion 2 of the sound insulation structure 1 faces the product portion 9 side and faces closely to the product portion 9, and the end face of the supporting wall portion 3 opposite the film portion 2 faces the base portion 8 side and faces closely to the base portion 8. However, although not shown, the film portion 2 of the sound insulation structure 1 may face the base portion 8 side and faces closely to the base portion 8, and the end face of the supporting wall portion 3 opposite the film portion 2 faces the product portion 9 side and faces closely to the product portion 9. The product portion 9 is made of a material having the same hardness as the film portion 2 and supporting wall portion 3 of the sound insulation structure 1 or harder than the film portion 2 and supporting wall portion 3, and has a dynamic storage modulus (E') of 1 MPa or more at 23° C. and a frequency of 1 Hz to 1000 Hz. 5 MPa or less. Specifically, the product part 9 may be made of a resin, a metal, a composite thereof, or the like.

[0040] The base portion 8 of the present embodiment has a thickness of 0.01 mm or more and 10 mm or less, and is made of a material having a hardness equal to or harder than that of the product portion 9. The dynamic storage modulus (E') at 23°C and at a frequency of 1 Hz to 1000 Hz is 1 MPa or more and 10 5 MPa or less. Specifically, the base 8 may be made of a resin, a metal, a composite of these, etc. One example is a 0.8 mm thick stainless steel plate that is generally used as a panel for an automobile body, etc.

[0041] In the soundproof structure 10 of this embodiment, the sound-insulating structure 1 may be disposed over the entire product part 9, or may be disposed over only a part of the product part 9. The membrane part 2 of the sound-insulating structure 1 may be joined to the product part 9 via an adhesive layer, or may not be joined to the product part 9. In addition, there may be a gap (air layer) between the sound-insulating structure 1 and the base part 8, or there may be no gap (air layer).

[0042] According to this soundproofing structure 10, since the soundproofing structure 1 is disposed between the base 8 and the product part 9, high soundproofing is obtained, and particularly excellent soundproofing is obtained in the frequency band of 400 Hz to 1000 Hz. In addition, since the support wall part 3 is flexible, the soundproofing structure 1 can be easily placed and held on the base 8 even if the base 8 is curved or uneven. As a result, this soundproofing structure 10 can be easily and stably installed on vehicles, equipment, etc. (for example, automobiles, trains, aircraft, ships, electronic parts, buildings, etc.). In addition, since the support wall part 3 is provided in the soundproofing structure 1 so as to divide the film part 2 into a plurality of sections 5, when a force is applied to press the film part 2 from the product part 9 side, the support wall part 3 abuts against the base 8 and acts as a support like a stick, so that the soundproofing structure 10 does not dent significantly. Therefore, a user who touches the product part 9 is prevented from feeling that the product part 9 dents significantly (sticky feeling).

[0043] Fig. 4(A) is a perspective view of the soundproofing structure 1 of the soundproofing structure 10 according to a modification of the first embodiment of the present invention, and Fig. 4(B) is a cross-sectional view of the soundproofing structure 10 cut along line AA in Fig. 4(A) and turned upside down. Fig. 5(A) is a cross-sectional view of the soundproofing structure 10 according to another modification, and Fig. 5(B) is a perspective view of the weight portion 4 of the soundproofing structure 1. Fig. 6(A) is a cross-sectional view of the soundproofing structure 10 according to yet another modification, and Fig. 6(B) is a perspective view of the weight portion 4 of the soundproofing structure 1. In these modifications, the spring portion 4a and the mass portion 4b of the weight portion 4 have different shapes and dimensions. In the modifications shown in Figs. 4(A) and 4(B), the spring portion 4a is a small-diameter cylindrical portion, and the mass portion 4b is a large-diameter cylindrical portion. In the modified example shown in Figs. 5(A) and 5(B), the spring portion 4a is elongated and cylindrical, the mass portion 4b is spherical, and the diameter of the cross-sectional shape of the cylindrical spring portion 4a is smaller than the diameter of the spherical mass portion 4b. In the modified example shown in Figs. 6(A) and 6(B), the spring portion 4a is truncated cone, the mass portion 4b is cylindrical, and the diameter of the smallest part of the truncated cone spring portion 4a is substantially equal to the diameter of the cylindrical mass portion 4b. In the modified example shown in Figs. 4(A) to 5(B), the mass portion 4b has a larger volume than the spring portion 4a. Therefore, even if the spring portion 4a and the mass portion 4b are made of the same material, the mass portion 4b has a larger mass than the spring portion 4a, and a spring-mass resonator can be formed. However, in this modified example, the spring portion 4a and the mass portion 4b may be made of different materials, and the mass portion 4b may have a larger mass than the spring portion. On the other hand, in the modified example shown in Figures 6(A) and 6(B), the spring portion 4a has a larger volume than the mass portion 4b. In this case, the mass portion 4b is made of a material having a higher density than the spring portion 4a, and the mass portion 4b has a larger mass than the spring portion, so that a spring-mass resonator can be formed. If the spring portion 4a has a truncated cone shape tapered in the direction away from the membrane portion 2 as in the modified example shown in Figures 6(A) and 6(B), the membrane portion 2 and the spring portion 4a can be easily releasable from a mold when they are integrally molded.

[0044] In this embodiment, the spring portion 4a and the mass portion 4b of the weight portion 4 are made different in either material or volume or both, so that the mass portion 4b has a larger mass than the spring portion 4a to configure a spring mass resonator and obtain a sufficient sound insulation effect. That is, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b are determined so that a spring mass resonator that can provide a sufficient sound insulation effect can be configured. As long as the mass of the mass portion 4b can be made larger than the spring portion 4a to the extent that a spring mass resonator that can provide a sufficient sound insulation effect can be configured in this way, the material, shape, and dimensions of the spring portion 4a and the mass portion 4b can be freely selected. However, the spring portion 4a needs to be made of a flexible material in order to function as a spring.

[0045] [Second embodiment] FIG. 7(A) is a perspective view of a soundproofing structure 6 of a soundproofing structure 11 according to a second embodiment of the present invention, and FIG. 7(B) is a cross-sectional view of the soundproofing structure 11 cut along line AA in FIG. 7(A) and turned upside down. The soundproofing structure 6 has a weight portion 7 of a single structure that is not divided into a spring portion and a mass portion. In this embodiment, a spring-mass resonator is configured in which the entire weight portion 7 functions as the mass portion and the film portion 2 functions as the spring portion. As an example, the mass of the weight portion 7 is about 0.1 g to 2.0 g. The material of the weight portion 7 is not limited, and it is formed of, for example, synthetic resin or metal. The other configurations are the same as those of the first embodiment described above, so that the description will be omitted. In the soundproofing structure 11 of this embodiment, the membrane vibration is also controlled by the action of the spring-mass resonator formed by the weight portion 7 and the film portion 2, and the membrane vibration is significantly reduced in a specific frequency range (for example, 400 Hz to 1000 Hz), and high sound insulation is exhibited. In addition, together with the membrane portion 2, the air in the space surrounded by the membrane portion 2 and the support wall portion 3 may function as a part of the spring of the spring mass resonator (air spring).

[0046] Both the membrane portion 2 and the supporting wall portion 3 of the sound-insulating structure 1 of this embodiment are made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a loss tangent (tan δ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz, and preferably having a dynamic storage modulus (E') of 0.05 MPa or more and 50 MPa or less at 23°C and a loss tangent (tan δ) of 0.05 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz.

[0047] The support wall 3 of this embodiment is made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity. Similarly, the membrane 2 of this embodiment is made of any one of a material having no energy elasticity but rubber elasticity, a material having no rubber elasticity but energy elasticity, and a material having both rubber elasticity and energy elasticity.

[0048] Fig. 8(A) is a cross-sectional view of a soundproof structure 11 according to a modification of the second embodiment of the present invention, and Fig. 8(B) is a perspective view of the weight 7 of the soundproof structure 6. In this modification, the weight 7 has a truncated cone shape that tapers away from the film 2. With this configuration, the film 2 and the weight 7 are easily releasable from a mold when they are integrally molded. In this embodiment, the shape of the weight 7 can be determined arbitrarily and is not particularly limited.

[0049] In any of the first and second embodiments, the film portion 2 and the supporting wall portion 3 can be formed by integral molding or two-color molding using the above-mentioned materials by injection molding, compression molding, press molding, extrusion molding, transfer molding, casting, etc. Furthermore, the weight portions 4, 7 can also be formed by integral molding, two-color molding, insert molding, etc. together with the film portion 2 and the supporting wall portion 3 using the above-mentioned materials. However, the sound-insulating structures 1, 6 may be assembled by first forming the film portion 2, the supporting wall portion 3, and the weight portions 4, 7 separately, and then joining them together by adhesion or heat fusion.

[0050] In the configuration of the sound insulation structures 1 and 6 described above, as shown in Figs. 9(A) and 9(B), the support wall 3 includes a plurality of first wall portions 3a extending in a first direction D1 parallel to the film portion 2 and a plurality of second wall portions 3b extending in a second direction D2 perpendicular to the first direction D1, and the planar shape of each section 5 is a square. In other words, the support wall portion 3 is a square tube having a square cross-sectional shape that defines each section 5, and a large number of square tube-shaped support walls 3 are arranged side by side, and the support walls 3 of adjacent sections 5 are integrated. However, the configuration is not limited to this. For example, as shown in Figs. 10(A) and 10(B), the planar shape of each section 5 may be a triangle, and the support wall portion 3 may be a square tube having a triangular cross-sectional shape that defines each section 5. As shown in Figs. 11(A) and 11(B), the planar shape of each section 5 may be pentagonal, and the support wall 3 may be a square tube having a pentagonal cross-sectional shape that defines each section 5. As shown in Figs. 12(A) and 12(B), the planar shape of each section 5 may be hexagonal, and the support wall 3 may be a square tube having a hexagonal cross-sectional shape that defines each section 5, forming a so-called honeycomb structure. Furthermore, as shown in Figs. 13(A) and 13(B), the planar shape of each section 5 may be circular, and the support wall 3 may be a cylinder having a circular cross-sectional shape that defines each section 5. In the case of the configuration shown in Figs. 11(A), 11(B), 13(A), and 13(B), gaps are generated between the sections 5, so it is preferable to determine the shape and dimensions of the support wall 3 so as to reduce the gaps. In the configurations shown in Figures 9(A), 9(B), 10(A), 10(B), 12(A), and 12(B), no gaps are generated between the compartments 5. Furthermore, each compartment 5 may have various shapes (not shown), such as a rectangle, a parallelogram, a trapezoid, a polygon with seven or more sides, an ellipse, an oval, or an irregular shape. The support wall portion 3 is formed to have a shape and dimensions that match the planar shape of each compartment 5.

[0051] The sound insulation structures 1, 6 of the soundproof structures 10, 11 of the present invention are very thin and lightweight, and can be easily placed on a curved or uneven surface, and are therefore well used when placed on the panel of a vehicle, particularly an automobile, as the base 8. An automobile panel, which is an example of the base 8, is basically a plate with no air permeability, and examples of such panels include metal plates (iron plates, steel plates, and aluminum plates) and resin plates. When the panel that is the base 8 on which the sound insulation structures 1, 6 are placed is a metal plate, its thickness is preferably in the range of 0.5 mm to 2.0 mm, and when it is a resin plate, its thickness is preferably in the range of 0.5 mm to 20 mm. When the sound insulation structures 1, 6 are placed on the base 8 (for example, the panel of an automobile), it is preferable that the end face of the support wall portion 3 of the sound insulation structures 1, 6 opposite to the side attached to the film portion 2 is placed on the panel. In this case, the support wall 3 and the base 8 may or may not be bonded to each other, but it is preferable that the support wall 3 is used by being placed on the base 8 without being bonded to the base 8. However, the end face of the support wall 3 and the base 8 may not be in contact with each other, and a gap (air layer) may exist between the sound insulation structures 1, 6 and the base 8.

[0052] Fig. 14(A) shows an automobile 12, which is an example of a vehicle in which the soundproofing structures 10 and 11 of the present invention are installed. The trunk portion 12a of Fig. 14(A) is shown in Fig. 14(B), the ceiling portion 12b of Fig. 14(A) is shown in Fig. 14(C), the front wheel surrounding portion 12c of Fig. 14(A) is shown in Fig. 14(D), and the door portion 12d of Fig. 14(A) is shown in Fig. 14(E). In the automobile 12 shown in Fig. 14(A), the soundproofing structures 10 and 11 of the present invention can be installed in the trunk side trim of the trunk portion 12a shown in Fig. 14(B), the roof lining of the ceiling portion 12b shown in Fig. 14(C), the fender liner of the front wheel surrounding portion 12c shown in Fig. 14(D), the door trim of the door portion 12d shown in Fig. 14(E), and the like. That is, examples of the base 8 which constitutes part of the soundproofing structures 10, 11 of the present invention and on which the sound-insulating structures 1, 6 are installed include interior materials of the automobile 12, such as roof lining, trunk side trim, door trim, pillar trim, engine head cover, back door trim, instrumental panel, floor carpet, dash insulator, hood insulator, etc.; exterior materials, such as undercovers and fender liners; and body panels, such as roof panels, dash panels, fender panels, hood panels, door inner panels, floor panels, back door panels, trunk panels, etc.In other words, in the engine compartment of the automobile 12, engine head covers, engine body covers, hood insulators, front dash insulators, air box walls, air intake cleaners, dust side ducts, under covers, etc.; in the cabin of the automobile, dash insulators, dash panels, floor carpets (floor silencers), spacers, door trims, inside of door trims, instrument panels, instrument center boxes, instrument upper boxes, air conditioner housings, roof trims, inside of roof trims, sun visors, etc. In the trunk of an automobile, the sound insulation structure 1,6 is installed on the trunk side trim, the inside of the trim, the drafter cover, etc. as the base 8, and the product part 9 is further arranged to cover the sound insulation structure 1,6, thereby forming the soundproof structure 10,11 having the sound insulation structure 1,6 sandwiched between the base 8 and the product part 9. The sound insulation structure 1,6 of the soundproof structure 10,11 of the present invention can also be installed inside the framework or between the panels of the automobile, and further, the soundproof structure 10,11 can be formed by installing the sound insulation structure 1,6 on the undercover under the floor located outside the vehicle, the fender protector, the back door, the wheel cover, the aerodynamic cover of the suspension, etc. as the base 8, and further by arranging the product part 9.

[0053] Specific examples and comparative examples of the soundproof structures 10 and 11 of the present invention will be described below. [Example 1] The soundproof structure 1 of the soundproof structure 10 of Example 1 of the present invention shown in Fig. 15 has the same structure as the first embodiment shown in Figs. 1 and 2. The film portion 2 is made of urethane rubber with a durometer A hardness of 30 according to JIS K6253 and a film thickness of 1.0 mm. The film portion 2 has a dynamic storage modulus (E') of 1.08 MPa at 23°C and a frequency of 1 Hz, and a loss tangent (tan δ) of 0.100 at 23°C and a frequency of 1 Hz. The planar shape of the film portion 2 has an area of ​​1000 cm 2 If the square shape is square, the bending stiffness K is 28.4 N / mm 2 and the axial stiffness k is 1.08×10 5 N / mm. The supporting wall 3 in this embodiment is made of urethane rubber with a durometer A hardness of 30 and a plate thickness of 1.2 mm. The height of the supporting wall 3 (the dimension in the direction perpendicular to the membrane portion 2) is 10 mm. The supporting wall 3 has a dynamic storage modulus (E') of 1.08 MPa at 23°C and a frequency of 1 Hz, and a loss tangent (tan δ) of 0.100 at 23°C and a frequency of 1 Hz. The axial rigidity k of the supporting wall 3 is 1.01×10 3 N / mm. However, the outermost supporting wall 3 alone has a plate thickness of half that, 0.6 mm. The compartments 5 defined by the multiple supporting walls 3 (first wall 3a and second wall 3b) are square, measuring 25 mm x 25 mm, and there are 49 compartments 5 in the 200 mm x 200 mm square area (evaluation surface) of the membrane 2. However, the drawing shows only a schematic portion of this area. The weight 4 is cylindrical, with a diameter of 6 mm and a height (dimension in the direction perpendicular to the membrane 2) of 6 mm.

[0054] Of the weight portion 4, the spring portion 4a, which is the portion attached to the membrane portion 2, is 3 mm in height and is made of an elastic body having a dynamic storage modulus (E') of 0.01 MPa or more and 100 MPa or less at 23°C and a frequency of 1 Hz to 1000 Hz, and a loss tangent (tan δ) of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. More specifically, the spring portion 4a in this embodiment has a dynamic storage modulus (E') of 0.60 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 1 Hz, a dynamic storage modulus (E') of 0.74 MPa and a loss tangent (tan δ) of 0.24 at 23° C. and a frequency of 10 Hz, a dynamic storage modulus (E') of 0.97 MPa and a loss tangent (tan δ) of 0.17 at 23° C. and a frequency of 100 Hz, and a dynamic storage modulus (E') of 1.31 MPa and a loss tangent (tan δ) of 0.16 at 23° C. and a frequency of 1000 Hz, and is made of silicone rubber with a durometer A hardness of 10 according to JIS K6253. The mass portion 4b, which is the portion of the weight portion 4 opposite to the side attached to the membrane portion 2, also has a height of 3 mm and is made of stainless steel (SUS304) having rigidity. The mass of the weight part 4 is about 0.8 g, and the resonance frequency of the weight part 4 is 600 Hz.

[0055] The product part 9 in this embodiment is a PP (polypropylene) film having a thickness of 1 mm. The base part 8 in this embodiment is a stainless steel plate having a thickness of 0.8 mm. The membrane part 2 of the sound insulation structure 1 is attached to the product part (PP film) 9 by an adhesive film 13 having a thickness of 85 μm. The adhesive film 13 is a PET (polyethylene terephthalate) film having a layer of silicone-based adhesive formed on one side and a layer of acrylic-based adhesive formed on the other side. The end face of the supporting wall part 3 of the sound insulation structure 1 opposite the membrane part 2 abuts against the base part 8. The overall height of the soundproof structure 10 of this embodiment thus constructed is 12.8 mm, and the surface density is 9.34 kg / m 2 It is.

[0056] The sound insulation of the soundproof structure 10 was measured with the side of the base 8 facing the sound insulation structure 1 and the opposite side as the incident sound side. Specifically, in accordance with the intensity method shown in JIS A1441-1, a test facility room with a reverberation room as the sound source room and a semi-anechoic room as the sound receiving room was used, and the sound transmission loss (transmission loss) [dB] was obtained for the 1 / 3 octave band center frequency [Hz] by 1 / 3 octave band analysis. The relationship between the 1 / 3 octave band center frequency and the sound transmission loss was obtained and is shown in Table 1 and Figures 16(A) to 16(B) and 17(A) to 17(B). The larger the sound transmission loss, the higher the sound insulation. In the 1 / 3 octave band center frequency [Hz] shown in Figures 16(A) to 16(B) and 17(A) to 17(B), 1 kHz is 1000 Hz, and the prefix "k" means 1000. The sound insulation was evaluated by comparing with the sound insulation calculated according to the mass law based on the mass of the soundproof structure 10 of this embodiment (the sound insulation of Comparative Example 1 described later).

[0057] [Table 1]

[0058] In addition to the sound insulation of the soundproof structure 10, the denting tendency (sticky feeling) was also evaluated. The denting tendency is the tendency of the product part 9 to deform when a load is applied from the product part 9 side to measure the stress generated when the product part 9 is deformed. The denting tendency was evaluated by a test using a sample of the soundproof structure 10 to be evaluated. Specifically, a plurality of sections 5 each having a side of 25 mm are formed by the support wall part 3 on the film part 2 having a side of 260 mm. The weight part 4 is not formed in the outermost section 5, and each section 5 in the range inside (a range having a side of 210 mm) has one weight part 4 formed. Instead of a stainless steel plate having a thickness of 0.8 mm as the base 8 of the soundproof structure 10, a test for evaluating the denting tendency was performed as follows. That is, as shown in FIG. 18, the soundproof structure 1 is placed on the base 8 so that the end face of the support wall part 3 opposite to the film part 2 abuts against the base 8, which is the base. The product part 9 is attached to the film part 2 of the soundproof structure 1 by an adhesive film 13. A load is applied from a predetermined position of the product part 9 using a push-pull gauge 14. As an example, the push-pull gauge 14 has a flat circular tip attachment with a diameter of 10 mm. When a load is applied using the push-pull gauge 14 and the deformation amount in the thickness direction of the product part 9 reaches a predetermined size (for example, 2 mm), the stress (N) displayed on the push-pull gauge 14 is measured. In this way, by dividing the stress (N) at the time when the deformation amount of the product part 9 reaches a predetermined size by the deformation amount (mm) of the product part 9, the stress required to deform the product part 9 by 1 mm, that is, the product part rigidity (N / mm), is obtained. The higher the product part rigidity, the less likely it is to be dented. Here, when the product part rigidity is 1 N / mm or more, it is considered that the denting tendency is small (no sticky feeling), and when it is less than 1 N / mm, it is considered that the denting tendency is large (sticky feeling). The results of evaluating the denting tendency of the soundproof structure 10 of Example 1 are shown in Table 1. Strictly speaking, the dent susceptibility was evaluated for soundproofing structure 10 having a different base 8 from that of Example 1, but the influence of base 8 on dent susceptibility is considered to be small, and the evaluation results are regarded as essentially representing the dent susceptibility of Example 1.

[0059] [Example 2] A soundproof structure 10 of Example 2 of the present invention has the same structure as that of the first embodiment shown in Figs. 1 and 2. The product part 9 of this example is a PP film having a thickness of 2 mm. The rest of the configuration is the same as that of Example 1, and the soundproof structure 1 and base part 8 of this example are the same as those of Example 1. The overall height of the soundproof structure 10 of this example is 13.8 mm, and the surface density is 10.2 kg / m 2 The sound insulation performance of the soundproof structure 10 of this embodiment was determined in the same manner as in Example 1, and is shown in Table 1 and FIG.

[0060] [Example 3] A soundproof structure 10 of Example 3 of the present invention has the same structure as that of the first embodiment shown in Figures 1 and 2. The product part 9 of this example is a low-density polyethylene (LDPE) film with a thickness of 1 mm. The rest of the configuration is the same as that of Example 1, and the soundproof structure 1 and base part 8 of this example are the same as those of Example 1. The overall height of the soundproof structure 10 of this example is 12.8 mm, and the surface density is 9.37 kg / m 2 The sound insulation of the soundproof structure 10 of this embodiment was determined in the same manner as in Example 1, and is shown in Table 1 and FIG.

[0061] [Example 4] The soundproof structure 10 of Example 4 of the present invention has the same structure as the first embodiment shown in Figs. 1 and 2. The product portion 9, base portion 8, and weight portion 4 of this example are the same as the product portion 9, base portion 8, and weight portion 4 of Example 1. The film portion 2 and supporting wall portion 3 of this example are made of urethane rubber having a durometer A hardness of 90 according to JIS K6253. The film portion 2 and supporting wall portion 3 have a dynamic storage modulus (E') of 30.1 MPa at 23°C and a frequency of 1 Hz, and a loss tangent (tan δ) of 0.115 at 23°C and a frequency of 1 Hz. The dimensions of the film portion 2 and supporting wall portion 3 are the same as those of the film portion 2 and supporting wall portion 3 of Example 1. The soundproof structure 10 of this example has an overall height of 12.8 mm and an areal density of 9.41 kg / m 2The sound insulation of the soundproof structure 10 of this embodiment was determined in the same manner as in Example 1, and is shown in Table 1 and Fig. 17(A). The dent susceptibility of the soundproof structure 10 of this embodiment was also evaluated in the same manner as in Example 1, and is shown in Table 1.

[0062] [Comparative Example 1] As Comparative Example 1, a theoretical value of sound insulation calculated based on the mass law in the case where a member having the same mass as the soundproof structure 10 of Example 1 is present is obtained and shown in Figures 16(A) to 16(B) and 17(A) to 17(B). This theoretical value of sound insulation becomes the evaluation standard of sound insulation in each Example and Comparative Example. The surface density in this Comparative Example is 9.34 kg / m 2 It is.

[0063] [Table 2]

[0064] [Comparative Example 2] As Comparative Example 2, as shown in Fig. 19, a soundproofing structure 15 without a product part 9 was constructed by placing a soundproofing structure 1 on a 0.8 mm thick stainless steel plate 8 that constituted a base 8. The base 8 and soundproofing structure 1 of this comparative example were the same as the base 8 and soundproofing structure 1 of Example 1. The overall height of the soundproofing structure 15 of this comparative example was 11.8 mm, and the surface density was 8.27 kg / m 2 The sound insulation of the soundproof structure 15 of this comparative example was determined in the same manner as in Example 1, and is shown in Table 2 and Fig. 16(A). Note that, since the soundproof structure 15 of this comparative example does not have a product part 9, the ease of denting was not evaluated.

[0065] [Comparative Example 3] In Comparative Example 3, as shown in Fig. 20, a product section 9 was placed on a 0.8 mm thick stainless steel plate 8, which was a base section 8, with a gap of 10 mm (air layer 16). The base section 8 and product section 9 of this comparative example were the same as the base section 8 and product section 9 of Example 1. The height of the entire structure of this comparative example was 11.8 mm, and the surface density was 6.98 kg / m 2The sound insulation of the structure of this comparative example was determined in the same manner as in Example 1, and is shown in Table 2 and Fig. 16(A). In addition, the ease of denting of the structure of this comparative example was evaluated in the same manner as in Example 1, and is shown in Table 2.

[0066] [Comparative Example 4] In Comparative Example 4, as shown in FIG. 21, a gap of 10 mm (air layer 16) and a rubber sheet 17 of 2 mm thickness were placed between the base 8, which was a 0.8 mm thick stainless steel plate, and the product part 9, which was a 1 mm thick PP film. The base 8 and product part 9 of this Comparative Example were the same as the base 8 and product part 9 of Example 1. The rubber sheet 17 was a material that has conventionally been used as a sound insulation material. The height of the entire structure of this Comparative Example was 13.8 mm, and the surface density was 9.50 kg / m 2 The sound insulation of the structure of this comparative example was determined in the same manner as in Example 1, and is shown in Table 2 and Fig. 17(B). The ease of denting of the structure of this comparative example was also evaluated in the same manner as in Example 1, and is shown in Table 2.

[0067] [result] The results of comparing the above-mentioned Examples 1 to 4 of the present invention with Comparative Examples 1 to 4 will be described. Referring to Figs. 16(A) to 17(B), it can be seen that all of the soundproof structures 10 of Examples 1 to 4 of the present invention have a greater sound insulation effect than the theoretical value based on the mass law (Comparative Example 1), particularly in the frequency band of 400 Hz to 1000 Hz. Comparing the sound insulation between Example 1 and Comparative Example 3 with Fig. 16(A), it can be seen that the soundproof structure 10 of the present invention has a greater sound insulation effect by having the sound insulation structure 1. Furthermore, comparing the sound insulation between Example 1 and Comparative Example 4 with Fig. 17(B), it can be seen that the soundproof structure 1 of the soundproof structure 10 of the present invention exhibits a greater sound insulation effect than a rubber sheet, which is one of the conventional sound insulation materials. Furthermore, comparing the sound insulation between Example 1 and Comparative Example 2 with Fig. 16(A), it can be seen that the soundproof structure 10 of the present invention has a greater sound insulation effect by having the product part 9.

[0068] On the other hand, when comparing the sound insulation of Examples 1 to 3 with reference to Fig. 16(A), it is found that a good sound insulation effect can be obtained even if the thickness and material of the product part 9 are slightly different. Also, when comparing the sound insulation of Examples 1 and 4 with reference to Fig. 17(A), it is found that when the film part 2 and the supporting wall part 3 of the sound insulation structure 1 are hard, a good sound insulation effect can be obtained and the tendency to dent is small (there is little tendency to become sticky).

[0069] As described above, according to the present invention, a soundproof structure can be obtained that has good sound insulation properties, particularly in the frequency band of 400 Hz to 1000 Hz, is less likely to be dented, and can be made thinner and lighter. This effect is exhibited in both the first embodiment shown in Figs. 1 to 6 and the second embodiment shown in Figs. 7 to 8.

[0070] The present invention may have the following configuration. [1] A sound insulation structure having a base, a product portion, and a sound insulation structure located between the base and the product portion, The sound-proof structure includes an elastic film portion, an elastic support wall portion standing on the film portion, and a weight portion standing on the film portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; Each of the weight portions constitutes a spring mass resonator having a spring portion having elasticity and a mass portion having a mass larger than that of the spring portion, A soundproofing structure characterized in that the membrane portion faces one of the product portion and the base portion, and the end face of the support wall portion opposite the membrane portion faces the other of the product portion and the base portion. [2] The soundproofing structure described in [1], wherein the membrane portion, the supporting wall portion and the spring portion are all made of either a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity. [3] The soundproof structure according to [1] or [2], wherein the membrane portion, the supporting wall portion and the spring portion all have a dynamic storage modulus of 0.01 MPa or more and 100 MPa or less at 23°C and at a frequency of 1 Hz to 1000 Hz. [4] A soundproof structure according to any one of [1] to [3], wherein the membrane portion, the supporting wall portion and the spring portion all have a loss tangent of 0.01 or more and 0.50 or less at 23°C and a frequency of 1 Hz to 1000 Hz. [5] A soundproofing structure described in any of [1] to [4], wherein the spring portion of the weight portion is located on the side of the weight portion that is attached to the membrane portion, and the mass portion is located on the side opposite the side of the weight portion that is attached to the membrane portion. [6] The soundproofing structure described in [5], wherein the mass portion of the weight portion has a larger volume than the spring portion. [7] A soundproofing structure described in any one of [1] to [6], wherein the mass portion of the weight portion is made of a material having a higher density than the spring portion. [8] A sound-insulating structure having a base, a product portion, and a sound-insulating structure located between the base and the product portion, The sound-proof structure includes an elastic film portion, an elastic support wall portion standing on the film portion, and a weight portion standing on the film portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; a spring mass resonator is configured with the membrane portion as a spring portion and the weight portion as a mass portion, A soundproofing structure characterized in that the membrane portion faces one of the product portion and the base portion, and the end face of the support wall portion opposite the membrane portion faces the other of the product portion and the base portion. [9] The soundproofing structure described in [8], wherein both the membrane portion and the supporting wall portion are made of either a material that does not have energy elasticity but has rubber elasticity, a material that does not have rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity.

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

[11] The soundproof structure according to

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

[12] A soundproofing structure described in any one of [1] to

[11] , wherein the thickness of the base is 0.01 mm or more and 10 mm or less.

[13] A soundproofing structure described in any of [1] to

[12] , wherein the membrane portion is adhered to the product portion by an adhesive film, and the end face of the supporting wall portion opposite the membrane portion faces the base in a contact or non-contact state.

[14] A soundproofing structure as described in any of [1] to

[13] , wherein the base is a panel of a vehicle and the product portion is a part of a product mounted inside the vehicle.

[15] A soundproofing structure described in any of [1] to

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

[16] A soundproofing structure described in any of [1] to

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

[17] The area of ​​each of said compartments is 100 mm 2 More than 1000mm2 A soundproofing structure according to any one of [1] to

[16] below.

[18] The area of ​​the membrane is 1000 cm 2 The soundproof structure according to any one of [1] to

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

[19] A soundproofing structure described in any one of [1] to

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

[20] A soundproofing structure described in any one of [1] to

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

[21] A soundproofing structure described in any one of [1] to

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

[22] A soundproofing structure described in any one of [1] to

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

[23] A soundproofing structure described in any one of [1] to

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

[24] A soundproofing structure according to any one of [1] to

[23] , wherein the membrane portion has a Durometer A hardness of 50 or more, and the support wall portion has a Durometer A hardness of 1 or more and 90 or less. [Explanation of symbols]

[0071] 1,6 Sound insulation structure 2 Membrane part 3 Support wall section 3a 1st wall 3b 2nd wall part 4,7 Weight 4a Spring part 4b Mass part 5 Plots 8 base 9 Product Department 10,11,15 Soundproofing 12. Automobiles 12a Trunk section 12b Ceiling section 12c Front wheel area 12d Door part 13 Adhesive film 14 Push-pull gauge 16 Air Layer 17 Rubber sheet

Claims

1. A sound insulation structure having a base, a product portion, and a sound insulation structure located between the base and the product portion, The sound-proof structure includes an elastic film portion, an elastic support wall portion standing on the film portion, and a weight portion standing on the film portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; Each of the weight portions constitutes a spring mass resonator having a spring portion having elasticity and a mass portion having a mass larger than that of the spring portion, A soundproofing structure characterized in that the membrane portion faces one of the product portion and the base portion, and the end face of the support wall portion opposite the membrane portion faces the other of the product portion and the base portion.

2. The soundproofing structure described in claim 1, wherein the membrane portion, the support wall portion and the spring portion are all made of either a material that has no energy elasticity but has rubber elasticity, a material that has no rubber elasticity but has energy elasticity, or a material that has both rubber elasticity and energy elasticity.

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

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

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

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

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

8. A sound insulation structure having a base, a product portion, and a sound insulation structure located between the base and the product portion, The sound-proof structure includes an elastic film portion, an elastic support wall portion standing on the film portion, and a weight portion standing on the film portion, the membrane portion is divided into a plurality of compartments by the support wall portion, the weight portion is located in each of the compartments or in some of the compartments, and in the compartments in which the weight portion is located, one weight portion is disposed in each of the compartments; a height of the support wall portion extending in a direction perpendicular to the membrane portion is greater than a height of the weight portion extending in a direction perpendicular to the membrane portion; a spring mass resonator is configured with the membrane portion as a spring portion and the weight portion as a mass portion, A soundproofing structure characterized in that the membrane portion faces one of the product portion and the base portion, and the end face of the support wall portion opposite the membrane portion faces the other of the product portion and the base portion.

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

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

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

12. 9. The soundproof structure according to claim 1, wherein the thickness of the base is 0.01 mm or more and 10 mm or less.

13. The soundproofing structure according to claim 1 or 8, wherein the membrane portion is adhered to the product portion by an adhesive film, and the end face of the supporting wall portion opposite the membrane portion faces the base portion in a contacting or non-contacting state.

14. 10. The acoustic structure of claim 1 or 8, wherein the base is a panel of a vehicle and the product portion is part of a product that is mounted inside the vehicle.

15. The soundproof structure described in claim 1 or 8, wherein the support wall portion includes a plurality of first wall portions extending in a direction perpendicular to the membrane portion and extending in a first direction parallel to the membrane portion, and a plurality of second wall portions extending in a direction perpendicular to the membrane portion and extending in a second direction perpendicular to the first direction.

16. 9. The soundproof structure according to claim 1 or 8, wherein the support wall portion is in the form of a cylinder having a circular, elliptical or oval cross-section that defines each of the compartments, or in the form of a square tube having a polygonal cross-section that defines each of the compartments.

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

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

19. 9. The soundproof structure according to claim 1, wherein the plate thickness of the support wall portion is 0.5 mm or more and 5.0 mm or less.

20. 9. The soundproof structure according to claim 1, wherein the film thickness of the film portion is 0.1 mm or more and 3.0 mm or less.

21. 9. The soundproof structure according to claim 1, wherein the height in a direction perpendicular to the membrane portion is 5 mm or more and 20 mm or less.

22. 9. The soundproof structure according to claim 1, wherein the height of the support wall portion extending in a direction perpendicular to the membrane portion is 5 mm or more and 20 mm or less.

23. 9. The soundproof structure according to claim 1, wherein the height of the weight portion extending in a direction perpendicular to the film portion is 1 mm or more.

24. 9. The soundproof structure according to claim 1, wherein the film portion has a durometer A hardness of 50 or more, and the support wall portion has a durometer A hardness of 1 or more and 90 or less.

Images