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WO2019138920A1 - Structure d'insonorisation, enceinte d'insonorisation et cellule d'insonorisation - Google Patents

Structure d'insonorisation, enceinte d'insonorisation et cellule d'insonorisation Download PDF

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Publication number
WO2019138920A1
WO2019138920A1 PCT/JP2018/048363 JP2018048363W WO2019138920A1 WO 2019138920 A1 WO2019138920 A1 WO 2019138920A1 JP 2018048363 W JP2018048363 W JP 2018048363W WO 2019138920 A1 WO2019138920 A1 WO 2019138920A1
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WO
WIPO (PCT)
Prior art keywords
hole
sound
fine
soundproof
surface plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/048363
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English (en)
Japanese (ja)
Inventor
昇吾 山添
真也 白田
知佳 松岡
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Fujifilm Corp
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Fujifilm Corp
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Filing date
Publication date
Application filed by Fujifilm Corp filed Critical Fujifilm Corp
Publication of WO2019138920A1 publication Critical patent/WO2019138920A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B3/00—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar shape; Layered products comprising a layer having particular features of form
    • B32B3/10—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar shape; Layered products comprising a layer having particular features of form characterised by a discontinuous layer, i.e. formed of separate pieces of material
    • B32B3/12—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar shape; Layered products comprising a layer having particular features of form characterised by a discontinuous layer, i.e. formed of separate pieces of material characterised by a layer of regularly- arranged cells, e.g. a honeycomb structure
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
    • E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
    • E04B1/62—Insulation or other protection; Elements or use of specified material therefor
    • E04B1/74—Heat, sound or noise insulation, absorption, or reflection; Other building methods affording favourable thermal or acoustical conditions, e.g. accumulating of heat within walls
    • E04B1/82—Heat, sound or noise insulation, absorption, or reflection; Other building methods affording favourable thermal or acoustical conditions, e.g. accumulating of heat within walls specifically with respect to sound only
    • E04B1/84—Sound-absorbing elements
    • E04B1/86—Sound-absorbing elements slab-shaped
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/162—Selection of materials
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/162—Selection of materials
    • G10K11/168—Plural layers of different materials, e.g. sandwiches
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects

Definitions

  • the present invention relates to a soundproofing structure, a soundproofing surrounding structure, and a soundproofing box, and more specifically, a sound absorbing body is provided on the outer surface of the face plate opposite to the honeycomb core of the two face plates sandwiching the honeycomb core.
  • the present invention relates to a disposed soundproof structure, a soundproof surrounding structure using the same, and a soundproof box.
  • a box using a honeycomb board as a wall material is lightweight and has high rigidity, it is used as a soundproof box that can be easily installed.
  • the sound absorbing material is not disposed inside the box, there is a problem that the reverberation in the box becomes large and a problem that the sound reflected inside the box leaks out of the box, so the soundproof performance of the box is deteriorated.
  • the soundproofness of the soundproof box is enhanced, but the volume inside the box is reduced.
  • the wall of such a box is constituted by a honeycomb structure, and one surface plate of the surface plate covering both sides of the honeycomb core is made a porous material (see Patent Document 1), or a plurality of It is set as a perforated surface plate provided with a through-hole, and weight reduction is achieved compared with the prior art by providing a sound absorbing material and / or a sound insulation material on this perforated surface plate (refer to patent documents 2, 3, 4, 5). And we aim at improvement of soundproofing performance such as sound absorption coefficient.
  • Patent Document 1 proposes a sound absorber in which a porous material made of a paper material having a predetermined porosity is disposed on a honeycomb utilizing Helmholtz resonance of the honeycomb.
  • Patent Document 2 proposes that a fine through-hole corresponding to a honeycomb cell is formed in a surface plate bonded on a honeycomb to constitute a Helmholtz sound absorbing structure, and further, to bond an unwoven fabric on the upper surface thereof. With this structure, the sound absorbing effect can be added while maintaining high rigidity, and the sound absorbing frequency band can be expanded by the non-woven fabric.
  • Patent Documents 3, 4 and 5 a fine through hole corresponding to a honeycomb cell is formed in a face plate adhered on a honeycomb to constitute a sound absorbing structure, and a sound absorbing material and / or a sound insulating material is further formed on the upper surface thereof. It is proposed to provide. With this structure, the sound insulation effect can be enhanced while maintaining high rigidity, and the sound insulation effect can be further enhanced by the sound absorbing material and / or the sound insulating material.
  • a soundproof panel for suppressing jet mixing noise and / or turbomachine noise in a fan duct of a turbofan aircraft engine and the like which is a surface sheet formed of a perforated plate and a metal cloth sheet
  • a thin and light-weight soundproof panel including a honeycomb core on the side of the core and a solid backing plate on the opposite side of the core.
  • the frequency band that can be soundproofed is narrow, and the sound insulation effect is further improved by the sound absorbing material and / or sound insulating material.
  • the band is expanded but there is a limit, and when trying to expand the band as described above, there is a problem that a thick sound absorbing material is required, and the thickness of the structure is greatly increased. That is, the sound absorbing structures disclosed in Patent Documents 1 to 6 have a problem that lightness, thinness, high rigidity and wide-range soundproofing can not be realized simultaneously.
  • the thickness and weight of the sound absorbing panel can be substantially smaller than that of the conventional sound absorbing panel, it is used for noise reduction of an aircraft engine
  • the problem is that metal materials are used, including metal cloth sheets, and it can not be said that they are sufficiently lightweight, and the hole diameter, thickness, sound absorber layer, etc. There is a problem that sufficient sound absorption characteristics can not be obtained.
  • the object of the present invention is to solve the above-mentioned problems of the prior art and to form a plurality of through holes in one of the face plates of the face plates on both sides of the honeycomb core and to face the honeycomb core of the face plate having through holes
  • a soundproof structure that is light in weight, thin, and capable of realizing both high rigidity and broad-band soundproofing.
  • Another object of the present invention is to provide a soundproof surrounding structure and a soundproofing box which is robust and lightweight, is capable of wide-band sound absorption, and has improved sound absorption performance by using the soundproof structure having the above effects. is there.
  • sound insulation includes the meanings of “sound insulation” and “sound absorption” as acoustic characteristics, but in particular means “sound insulation”.
  • sound insulation refers to “shielding the sound”. That is, “sound insulation” means “do not transmit sound”. Therefore, “sound insulation” means including “reflecting” sound (reflection of sound) and “absorbing” sound (absorption of sound) (Sanshodo Daijinrin (third edition), and Japanese acoustics) See the materials society web page http://www.onzai.or.jp/question/soundproof.html, and http://www.onzai.or.jp/pdf/new/gijutsu201312_3.pdf). In the following, basically, “reflection” and “absorption” are not distinguished, but both are referred to as “sound insulation” and “shielding”, and when both are distinguished, “reflection” and “absorption” are said. .
  • the soundproof structure comprises a honeycomb core, a first face plate sandwiching the honeycomb core, and a second face plate, and a through-hole perforated in the first face plate.
  • a sound absorber disposed on the outer surface of the first face plate opposite to the honeycomb core, and the diameter of the through hole of the first face plate is 1.0 mm or more, and the opening of the through hole
  • the ratio is 1.0% or more, and when the thickness of the honeycomb core is l, the thickness of the first surface plate is h, and the opening ratio is ar, the condition of the following inequality (1) is satisfied.
  • f 1 (l, h) ⁇ ln (ar) + f 2 (l, h) ⁇ 1.5
  • f 1 (l, h) A 1 (h) ⁇ l 2 + A 2 (h) ⁇ l + 0.24915
  • f 2 (l, h) A 3 (h) ⁇ l 2 + A 4 (h) ⁇ l + 1.804
  • a 1 (h) 19.466 ⁇ ln (h) -0.3038
  • a 2 (h) ⁇ 1.611 ⁇ ln (h) +4.0162
  • a 3 (h) 119.22 ⁇ ln (h) +78.249
  • a 4 (h) -5689.7 ⁇ h + 94.861
  • the sound absorber is preferably a porous material.
  • the sound absorber is preferably made of a fine through hole plate, a woven cloth, a knitted cloth or a non-woven cloth, and more preferably a woven cloth or a knitted cloth.
  • the sound absorber preferably has a plurality of fine through holes penetrating in the thickness direction, and the diameter of the fine through holes is preferably 250 ⁇ m or less.
  • the upper limit is rho_center + (0.795 ⁇ (phi / 30) -2) with the lower limit of rho_center ⁇ (0.052 ⁇ (phi / 30) ⁇ 2).
  • the thickness of the sound absorber is preferably 50 mm or less. Moreover, 25 mm or less is more preferable, 5 mm or less is still more preferable, 2 mm or less is still more preferable, and 1 mm or less is the most preferable.
  • the honeycomb core is preferably made of paper, metal or resin.
  • the second front plate is preferably made of paper, metal or resin.
  • the first front plate is made of paper, metal or resin.
  • the honeycomb core, the first front plate, and the second front plate are made of paper, and the sound absorber is made of a woven cloth or a knitted cloth.
  • the aperture ratio of the through-hole in a 1st surface board is 5.0% or more.
  • the aperture ratio of the through-hole in a 1st surface board it is more preferable that it is 10% or more.
  • the aperture ratio of the through-hole in a 1st surface board is 20% or more.
  • aeration flow resistance of the sound absorber is 10 to 50000 Rayls (Pa ⁇ s / m or N ⁇ s / m 3 , hereinafter, only Rayls is described). Further, the total throughflow resistance of the throughflow portion R1 of the through hole of the first surface plate and the throughflow resistance R2 of the sound absorber is 12 Rayls or more and preferably 16700 Rayls or less. Further, the total aeration flow resistance is 75 Rayls or more, more preferably 2570 Rayls or less, and more preferably 150 Rayls or more, and most preferably 1150 Rayls or less.
  • a cover layer is provided on the sound absorber, and the total flow resistance of the air flow resistance R1 of the through hole portion of the first face plate, the air flow resistance R2 of the sound absorber and the air flow resistance R3 of the cover layer is It is preferably 12 Rayls or more and 16700 Rayls or less. Further, the total aeration flow resistance is 75 Rayls or more, more preferably 2570 Rayls or less, and more preferably 170 Rayls or more, and most preferably 1150 Rayls or less. Moreover, it is preferable that the flow resistance per unit length of a sound absorbing body is 5000 Rayls / m or more.
  • the through-hole of two or more different hole diameters is opened by the 1st surface board.
  • the first surface plate further has a small through hole having a diameter smaller than that of the through hole and having an opening ratio of less than 1.0%.
  • the soundproofing surrounding structure of the 2nd aspect of this invention uses 2 or more of the soundproofing structures of the said 1st aspect.
  • the soundproof box of the 3rd aspect of this invention has a soundproof surrounding structure of the said 2nd aspect.
  • the soundproof box of the third aspect of the present invention comprises the soundproof structure of the first aspect.
  • a ventilating port for intake and exhaust be arranged.
  • the diameter of the fine through holes is preferably 1.0 ⁇ m or more.
  • the material of a fine through-hole board is a flame retardant material.
  • the flame retardant material is preferably metal.
  • the metal is preferably aluminum or an aluminum alloy.
  • a sound absorbing body has a deodorizing function, a waterproof function, or a water repellent function.
  • the present invention it is possible to provide a soundproof structure capable of realizing both light weight, thinness, high rigidity and wide-range soundproofing. Furthermore, according to the present invention, it is possible to realize a soundproof surrounding structure and a soundproof box that are robust and lightweight, can perform wide-range sound absorption, and have improved sound absorption performance. Further, according to the present invention, it is possible to improve the appearance and the like.
  • FIG. 1 It is a fragmentary sectional view showing typically an example of a soundproofing structure concerning one embodiment of the present invention. It is a top view which partially fractures and shows the soundproofing structure shown in Drawing 1 typically. It is sectional drawing which shows typically an example of the resonance structure used for this invention. It is a graph showing the aperture ratio dependence of the normal incidence sound absorption coefficient of the resonance structure shown in FIG. It is a graph showing the spectrum of the sound pressure of the resonance structure shown in FIG. It is an example of the graph showing the noise level with respect to the aperture ratio of the resonance structure shown in FIG.
  • FIG. 7 is a cross-sectional view schematically showing a soundproof structure of Comparative Example 1; It is a graph which shows the relationship of the normal incidence sound absorption coefficient of the soundproof structure of Example 1-3 of this invention, and Comparative Examples 1-2, and a frequency. It is a graph which shows the relationship of the noise level and aperture ratio of the soundproof structure of Examples 1 to 3 and Comparative Example 1 of the present invention. It is a graph which shows the relationship of the normal incidence sound absorption coefficient of the soundproof structure of Example 4-6 of this invention, and Comparative Examples 1 and 3, and a frequency.
  • FIG. 1 shows typically the soundproof structure of Example 12 shown in FIG.
  • FIG. 21 is a top view schematically showing a soundproof structure of Comparative Example 11; It is a side view which shows typically the soundproof structure of the comparative example 11 shown in FIG. It is a graph which shows the relationship of the normal incidence sound absorption coefficient of the soundproof structure of Example 11-12 of this invention, and the comparative example 11, and a frequency. It is a top view which shows typically an example of the sound-insulation structure which concerns on other embodiment of this invention. It is a side view which shows the soundproofing structure shown in FIG. 22 typically. It is a graph which shows the relationship of the normal incidence sound absorption coefficient of the soundproof structure of Example 21 of this invention, and a frequency.
  • a soundproof structure a soundproof surrounding structure using the same, and a soundproof box according to the present invention will be described in detail based on preferred embodiments shown in the attached drawings.
  • a numerical range represented using “to” means a range including numerical values described before and after “to” as the lower limit value and the upper limit value.
  • the soundproof structure according to the first embodiment of the present invention includes a honeycomb core, a first surface plate sandwiching the honeycomb core, a second surface plate, a through hole perforated in the first surface plate, and a honeycomb of the first surface plate. And a sound absorber disposed on the outer surface opposite to the core, wherein the diameter of the through hole in the first face plate is 1.0 mm or more, and the aperture ratio of the through hole is 1.0% or more is there.
  • the soundproof structure of the present invention can realize light weight, high rigidity, and broad-band soundproofing.
  • the soundproofing structure of the present invention is robust and lightweight, can perform broad-band sound absorption, and can realize a soundproof surrounding structure and a soundproof box with improved sound absorption performance.
  • the soundproof structure of the present invention not only reduces the reverberation inside the soundproof box, but can also reduce the volume that leaks out.
  • the soundproof structure of the present invention can constitute a soundproof box with a simple box configuration by enhancing the sound absorption performance of the wall.
  • the soundproof structure of the present invention is, for example, inside or outside of a building or other structure (for example, a house, a hall, an elevator, a music classroom, a wall such as a meeting room, and a panel for ceiling), It can be used for transportation applications such as interior construction of automobiles, and for logistics applications such as box materials and packaging materials. Further, the soundproof structure of the present invention can be used for other copying machines, blowers, air conditioners, ventilating fans, pumps, generators, ducts and the like.
  • the soundproof structure of the present invention further includes industrial machines such as coating machines in factories and the like, various types of manufacturing equipment that emits sounds such as rotary machines and transport machines, vehicles such as automobiles, and trains, Used in general household appliances such as refrigerators, washing machines, dryers, televisions, copiers, microwave ovens, game machines, air conditioners, fans, PCs (personal computers), vacuum cleaners, air purifiers, and ventilation fans be able to.
  • the soundproof structure of this invention is suitably arrange
  • FIG. 1 is sectional drawing which shows typically an example of the sound-insulation structure which concerns on 1st Embodiment of this invention.
  • FIG. 2 is a top view schematically showing the soundproof structure shown in FIG. 1 partially broken.
  • the soundproof structure 10 of the present invention comprises a honeycomb core 12 having a plurality of openings 14, a plate-like first surface plate 16 having a plurality of through holes 18, and a second surface.
  • a face plate 20 and a sound absorber 22 are provided.
  • the first front plate 16 and the second front plate 20 are arranged to sandwich the honeycomb core 12 with a space therebetween.
  • the first surface plate 16 is bonded to one surface of the honeycomb core 12.
  • the second surface plate 20 is bonded to the other surface of the honeycomb core 12.
  • a sound absorber 22 is disposed on the outer surface of the first face plate 16 (ie, one face of the first face plate opposite to the honeycomb core 12).
  • the sound absorbing body 22 is composed of a fine through hole plate 26 having a plurality of fine through holes 24 in the illustrated example.
  • FIG. 2 in order to make the structure of the soundproof structure 10 easy to understand, a portion where the first surface plate 16 and the sound absorber 22 (fine through hole plate 26) are broken is shown on the left side of FIG. A portion where only the (fine through hole plate 26) is broken is shown in the middle of FIG.
  • the honeycomb core 12 is disposed between the first front plate 16 and the second front plate 20, is a frame having a plurality of honeycomb cells (frames), and has a plurality of openings 14 penetrating in the thickness direction. Have. That is, each honeycomb cell (frame) has an opening 14 respectively.
  • the plurality of openings 14 of the honeycomb core 12 are closed by the first front plate 16 and the second front plate 20 disposed on both sides. Behind the through holes 18 of the first face plate 16, the openings 14 of the honeycomb core 12 are closed and a back air layer is formed.
  • arranging a plurality of through holes 18 with respect to the first surface plate 16 so that one through hole 18 of the first surface plate 16 corresponds to one opening 14 of the honeycomb core 12.
  • the plurality of through holes 18 of the first front plate 16 be arranged in one-to-one correspondence with the plurality of openings 14 of the honeycomb core 12 respectively.
  • the plurality of through holes 18 are also regularly arranged in the first surface plate 16 according to the regular arrangement of the plurality of openings 14. Of course it is done.
  • the arrangement of the plurality of openings 14 of the honeycomb core 12 and the arrangement of the plurality of through holes 18 of the first surface plate 16 are not limited to those described above.
  • the two or more through holes 18 of the first surface plate 16 may be arranged to correspond to the openings 14 of the honeycomb core 12.
  • the plurality of openings 14 may not be regularly arranged in the honeycomb core 12.
  • the honeycomb core 12 preferably has a honeycomb structure. That is, the shape of the opening 14 is preferably a honeycomb (regular hexagonal) shape in a planar shape, but it is not particularly limited in the present invention.
  • the shape of the opening 14 may be a circle, an ellipse, a square (square), another rectangle such as a rectangle, a rhombus, or a parallelogram, a triangle such as an equilateral triangle, an isosceles triangle, or a right triangle.
  • it may be a polygon including a regular polygon such as a regular octagon, an ellipse or the like, or it may be indeterminate.
  • the diameter (pore diameter or size) of the opening 14 is the distance between opposing sides passing through the center or the circle equivalent diameter It can be defined, and in the case of a polygon, an ellipse, or an irregular shape, it can be defined as a circle equivalent diameter.
  • the equivalent circle diameter and the radius are respectively the diameter and the radius when converted to a circle having the same area.
  • the diameter (pore diameter, size) of the opening 14 of the honeycomb core 12 is larger than the diameter of the through hole 18 of the first surface plate 16.
  • the diameter of the opening 14 can be said to be the size (for example, the width or the length) of the honeycomb cells of the honeycomb core 12.
  • the diameter of the opening 14 is preferably 1.0 mm to 500 mm, more preferably 5 mm to 250 mm, and particularly preferably 10 mm to 100 mm.
  • the reason why the diameter of the opening 14 is preferably 1.0 mm to 500 mm is that if it is smaller than 1.0 mm, the air viscosity resistance at the side wall of the cylindrical honeycomb core 12 becomes high, and the sound absorption effect decreases. Also, it is difficult to manufacture.
  • the aperture ratio of the openings 14 of the honeycomb core 12 is larger than the aperture ratio of the through holes 18 of the first surface plate 16.
  • the shape and / or diameter of the openings 14 (or honeycomb cells) may be the same and constant in all the openings 14 (or honeycomb cells), but may be different and different sizes ( Openings (honeycomb cells) of different shapes may also be included.
  • the planar shape and the size (planar size) of the honeycomb core 12 are not particularly limited, and may be appropriately determined in accordance with the planar shape, the size, and the like of the first surface plate 16 or the second surface plate 20. And choose.
  • the thickness of the honeycomb core 12 is equal to the distance (separation distance) between the sound absorber 22 and the second surface plate 20.
  • the thickness of the honeycomb core 12 is not particularly limited, and may be determined or selected according to the place where the soundproof structure 10 of the present invention is used and the environment.
  • the thickness of the honeycomb core 12 is, for example, preferably 1.0 mm to 200 mm, more preferably 5 mm to 100 mm, and particularly preferably 10 mm to 50 mm.
  • the reason why the thickness of the honeycomb core 12 is preferably 1.0 mm to 200 mm is that the rigidity is greatly reduced when the thickness is less than 1.0 mm, and when the thickness is more than 200 mm, the soundproof structure becomes thicker. However, there is no space for placement.
  • the material of the honeycomb core 12 is lightweight and has high rigidity, and the honeycomb core 12 can support the first surface plate 16 and the sound absorber 22, and the first surface plate 16 and the second surface plate 20 It is not particularly limited as long as the distance between the two can be maintained constant and the air column resonance structure can be configured with the second face plate 20.
  • the material of the honeycomb core 12 may be, for example, a flammable material or a flame retardant material.
  • the flammable material refers to materials other than the following flame retardant materials, and examples thereof include resin materials such as paper, wood, and synthetic resin. Examples of paper include cardboard, boards and the like.
  • the resin material examples include acrylic resin such as polymethyl methacrylate (PMMA), polyethylene terephthalate (PET), polycarbonate, polyamideid, polyarylate, polyetherimide, polyacetal, polyetheretherketone, polyphenylene sulfide, polysulfone, poly Examples include butylene terephthalate, polyimide, and triacetyl cellulose.
  • acrylic resin such as polymethyl methacrylate (PMMA), polyethylene terephthalate (PET), polycarbonate, polyamideid, polyarylate, polyetherimide, polyacetal, polyetheretherketone, polyphenylene sulfide, polysulfone, poly Examples include butylene terephthalate, polyimide, and triacetyl cellulose.
  • PMMA polymethyl methacrylate
  • PET polyethylene terephthalate
  • PET polycarbonate
  • polyamideid polyarylate
  • polyetherimide polyacetal
  • polyetheretherketone polyphenylene sulf
  • a flame retardant material refers to a material other than the above-mentioned combustible material, but in the case of a building material, a non-combustible material defined in Building Standard Act Article 2, Item 9, Building Standard Act Enforcement Order 1 Refers to the quasi-combustible materials specified in item 5 and the flame-retardant materials specified in Article 1 item 6 of the same Article. These materials do not burn for more than 5 minutes after the start of heating when heat from a normal fire is applied, they do not cause deformation, melting, cracking and other damage harmful to fire protection, harmful to evacuation It is necessary to satisfy three points of no smoke or no gas generation.
  • materials such as a metal material, an inorganic material, a flame-retardant plywood, a flame-retardant fiber board, and a flame-retardant plastic board, can be mentioned, for example.
  • a metal material aluminum, steel, titanium, magnesium, tungsten, iron, steel, chromium, chromium molybdenum, nichrome molybdenum, and these alloys etc. can be mentioned, for example.
  • As an inorganic material glass, concrete, a gypsum board, sapphire, ceramics, etc. can be mentioned, for example.
  • it can be used as a flame retardant material by coating a flammable material with an aramid resin or the like.
  • honeycomb core 12 As a material of honeycomb core 12 other than these, the material containing carbon fiber, such as carbon fiber reinforced plastic (CFRP), carbon fiber, and glass fiber reinforced plastic (GFRP), can also be mentioned. In addition, you may use combining the multiple types of material of these honey-comb cores 12. As shown in FIG. It is preferable to use a metal such as aluminum as the material of the honeycomb core 12 because high fire resistance can be obtained. On the other hand, using paper as the material of the honeycomb core 12 is preferable because it can be easily incinerated and can be made lighter. In addition, it is preferable to use a paper coated with an aramid resin because light weight and fire resistance can be obtained. From the above, the honeycomb core 12 is preferably made of paper, metal, or resin.
  • CFRP carbon fiber reinforced plastic
  • GFRP glass fiber reinforced plastic
  • the thickness of the material of the honeycomb core 12 is such that the honeycomb core 12 is light in weight and has high rigidity, and has rigidity capable of supporting the first surface plate 16 and the sound absorber 22.
  • the thickness of the material of the honeycomb core 12 is, for example, preferably 0.001 mm (1 ⁇ m) to 5 mm, more preferably 0.01 mm (10 ⁇ m) to 2 mm, and 0.1 mm (100 ⁇ m) to 1.0 mm Is particularly preferred.
  • the reason why the thickness of the material of the honeycomb core 12 is preferably 0.001 mm (1 ⁇ m) to 5 mm is that if it is less than 0.001 mm (1 ⁇ m), the rigidity decreases. If it exceeds 5 mm, the weight becomes heavy, and the weight merit of the honeycomb is lost. Even if a sound absorbing material such as a woven cloth, a knitted cloth, a non-woven fabric, or a sound absorbing material made of fibers such as felt or a porous material such as urethane is disposed in the openings (honeycomb cells) 14 of the honeycomb core 12. good. In addition, a sound absorber may be provided between the honeycomb core 12 and the first surface plate 16.
  • the first surface plate 16 and the honeycomb core 12 and the honeycomb core 12 and the second surface plate 20 are preferably fixed without a gap. If the method of fixing the first surface plate 16 and the honeycomb core 12 and the method of fixing the honeycomb core 12 and the second surface plate 20 are as long as the honeycomb core 12 and the first surface plate 16 and the second surface plate 20 can be fixed. Anything may be used, and it is not particularly limited.
  • the fixing method may include, for example, a method using an adhesive or a method using a physical fixing tool. In the method of using an adhesive, the adhesive is applied on both surfaces (of the honeycomb cell) surrounding the opening 14 of the honeycomb core 12 and the first surface plate 16 and the second surface plate 20 are respectively applied thereon. Are placed and fixed to the honeycomb core 12.
  • the adhesive for example, epoxy-based adhesive (Araldite (registered trademark) (manufactured by Nichiban Co., Ltd.) and the like), cyanoacrylate-based adhesive (Aron Alpha (registered trademark) (manufactured by Toagosei Co., Ltd. and the like), and acrylic An adhesive etc. can be mentioned.
  • the first surface plate 16 disposed so as to cover and sandwich the opening 14 of the honeycomb core 12 and the second surface plate 20 are made of the honeycomb core 12 and fixing members such as rods.
  • a method of fixing the fixing member to the honeycomb core 12 using a fixing tool such as a screw or a screw can be cited.
  • the first surface plate 16 has a plate shape and has a plurality of through holes 18 penetrating in the thickness direction.
  • the plurality of through holes 18 of the first surface plate 16 are covered by the sound absorbers 22 disposed on the first surface plate 16 and thus become invisible.
  • the through holes 18 of the first surface plate 16 correspond to the openings 14 of the honeycomb core 12. Behind the through holes 18 of the first face plate 16, the honeycomb core 12 and the second face plate 20 form a back air layer in a closed space.
  • the honeycomb core 12 forming the through holes 18 of the first surface plate 16 and the back air layer behind the same, and the second surface plate 20 constitute an air column resonance structure.
  • the portion of the honeycomb core 12 having one opening 14 and the portion of the second face plate 20 corresponding to the one opening 14 constitute an air column resonance structure.
  • air column resonance occurs which is determined by the length of the air column of the honeycomb core 12.
  • the through holes 18 of the first face plate 16 are large holes that do not interfere with air column resonance (do not induce Helmholtz resonance).
  • the sound absorbing body 22 does not constitute air column resonance itself, but is for adding resistance to the air column resonance structure to widen a sound absorbing zone.
  • the plurality of through holes 18 may be arranged in the first surface plate 16, it may be regularly arranged according to the plurality of openings 14 of the honeycomb core 12. preferable.
  • One through hole 18 may be provided in the first surface plate 16.
  • the thickness of the first surface plate 16 is not particularly limited as long as the through holes 18 do not induce Helmholtz resonance and can support the sound absorber 22.
  • the thickness of the first surface plate 16 is, for example, preferably 0.001 mm (1 ⁇ m) to 5 mm, more preferably 0.01 mm (10 ⁇ m) to 2 mm, and 0.1 mm (100 ⁇ m) to 1.0 mm Is particularly preferred.
  • the planar shape and the size (planar size) of the first front plate 16 are not particularly limited, and may be appropriately determined according to the place where the soundproof structure 10 using the first front plate 16 is used, the environment, and the like. You just have to choose it.
  • the plurality of through holes 18 of the first surface plate 16 are preferably arranged to correspond to the plurality of openings 14 of the honeycomb core 12 respectively.
  • one through hole 18 of the first surface plate 16 and one opening 14 of the honeycomb core 12 be arranged in one-to-one correspondence.
  • the present invention is not limited thereto, and if it does not disturb the air column resonance constituted by the honeycomb core 12 and the second surface plate 20 (does not induce the Helmholtz resonance), one opening of the honeycomb core 12 Two or more through holes 18 may be provided to 14.
  • the plurality of through holes 18 of the first front plate 16 be regularly arranged.
  • the shape of the through hole 18 is preferably planar and circular, but is not particularly limited in the present invention.
  • the shape of the through hole 18 may be a square (square), another rectangle such as a rectangle, a rhombus, or a parallelogram, a triangle such as an equilateral triangle, an isosceles triangle or a right triangle, an equilateral pentagon, or an equilateral hexagon It may be a polygon including a regular polygon, or an ellipse or the like, or it may be indeterminate.
  • the diameter (pore diameter, size) of the through hole 18 can be defined in the same manner as the diameter (pore diameter, size) of the opening 14.
  • the diameter of the through hole 18 of the first surface plate 16 needs to be 1.0 mm or more, preferably 5 mm or more, and more preferably 10 mm or more.
  • the diameter of the through hole 18 is preferably 100 mm or less, more preferably 50 mm or less, and particularly preferably 25 mm or less.
  • the diameter of the through hole 18 of the first surface plate 16 is 1.0 mm or more, and the aperture ratio of the through hole 18 needs to be 1.0% or more.
  • Helmholtz resonance consisting of the air weight of the through hole 18 of the first surface plate 16 and the air spring by the honeycomb core 12 hardly occurs, and the air column length of the honeycomb core 12 A fixed air column resonance occurs to enable sound absorption in a wide band.
  • the reason for limiting the diameter of the through hole 18 to 1.0 mm or more is that, when the diameter of the through hole 18 is smaller than 1.0 mm, the viscous resistance at the side wall of the through hole 18 becomes large, and the sound absorber 22 becomes the first surface plate If it is disposed on the 16 through holes 18, the acoustic resistance becomes too large, and the sound absorption characteristic is deteriorated.
  • the reason for limiting the preferable range of the diameter of the through hole 18 to 100 mm or less is because the rigidity of the soundproof structure is lowered when the diameter is larger than 100 mm.
  • the shape and / or diameter of the through holes 18 may be constant in all the through holes 18, but may include different sizes (including different shapes). That is, through holes 18 of two or more different hole diameters may be opened (perforated) in the first surface plate 16.
  • the first surface plate 16 may have small through holes having a diameter smaller than that of the through holes 18 and having an opening ratio of less than 1.0%.
  • the diameter of the through hole 18 of the first surface plate 16 is larger than the diameter of the fine through hole 24 of the fine through hole plate 26 which is the sound absorbing body 22, and the penetration of the first surface plate 16 is also possible.
  • the aperture ratio of the holes 18 is larger than the aperture ratio of the fine through holes 24 of the sound absorber 22.
  • the opening ratio of the through holes 18 of the first surface plate 16 is the ratio of the area of the through holes 18 to the area of the closed space (back air layer) described above, that is, the cross sectional area of the honeycomb cells of the honeycomb core 12 (the area of the openings 14). It can be defined as the ratio of the hole area of the through hole 18 of the first front plate 16 to the When the openings 14 of the honeycomb core 12 are not constant or when the through holes 18 are not constant, the aperture ratio of the through holes 18 can be defined as the average aperture ratio of the through holes 18.
  • the average aperture ratio of the through holes 18 can be determined as the total area ratio of all through holes 18 (the ratio of the total area of all through holes 18) to the area of the entire opening 14 of the honeycomb core 12.
  • the area of all the openings 14 of the honeycomb core 12 may be obtained from the product of the average diameter and the number by calculating the average diameter and the number of the all openings 14 within the predetermined range of the honeycomb core 12. Further, the area of all the through holes 18 of the first surface plate 16 may be determined from the product of the average diameter and the number by calculating the average diameter and the number of all the through holes 18 within the predetermined range of the first surface plate 16 .
  • the aperture ratio of the through hole 18 needs to be 1.0% or more.
  • the opening ratio of the through holes 18 is preferably 5.0% or more, more preferably 10% or more, and still more preferably 20% or more.
  • the reason why the aperture ratio is 1.0% or more is that, when the aperture ratio of the through hole 18 of the first surface plate 16 is 1.0% or more, the air weight by the air weight of the through hole 18 and the honeycomb core 12 This is because Helmholtz resonance consisting of a spring hardly occurs, air column resonance determined by the length of the air column of the honeycomb core occurs, and sound absorption in a wide band becomes possible.
  • an aperture ratio of 10% or more is preferable.
  • the opening ratio is preferably 90% or less, more preferably 80% or less, still more preferably 70% or less, and particularly preferably 50% or less.
  • the reason why the opening ratio of the through holes 18 is preferably 5.0% or more can be considered as follows.
  • the dependence of the aperture ratio (the ratio of the area of the through hole to the area of the closed space) of the normal incidence sound absorption coefficient of the resonance structure as shown in FIG. I calculated how much the level went down.
  • the resonance structure 28 shown in FIG. 3 can also be said to be the one cell of the soundproof structure 10 of the present invention shown in FIG.
  • the resonant structure 28 has a honeycomb core 12 having an opening 14, a first face plate 16 having a through hole 18, and a second face plate 20.
  • a indicates the radius of the through hole 18
  • w indicates the diameter of the opening 14
  • h indicates the thickness of the first surface plate 16
  • l indicates the thickness of the honeycomb core 12.
  • the radius a of the through hole 18 is 0.0005 m (0.5 mm)
  • the thickness l of the honeycomb core 12 is 0.03 m (30 mm)
  • the thickness h of the first surface plate 16 is 0.. This is the case of 001 m (1 mm). It can be seen that as the aperture ratio ar increases, the frequency of the peak of the normal incidence sound absorption coefficient shifts to the high frequency side, and the band spreads.
  • FIG. 6A One of the results is shown in FIG. 6A as a representative.
  • the thickness l of the honeycomb core 12 is 0.03 m (30 mm), and the thickness h of the first surface plate 16 is 0.001 m (1 mm).
  • the noise level of pink noise sharply decreases as the aperture ratio increases. From this result, it can be said that the broad band sound absorption of the air column resonance has a higher muffling effect than the narrow band sound absorption characteristics at low frequencies of the Helmholtz resonance. From the graph shown in FIG. 6A, it can be seen that when the aperture ratio is 5.0%, the noise level rapidly decreases and the muffling effect increases.
  • the aperture ratio is preferably 5.0% or more. Also, it can be seen that at 10%, the noise level falls sharply further, and the silencing effect becomes greater. Therefore, it is understood that the aperture ratio is more preferably 10% or more. Further, it can be seen that at 20%, the noise level decreases even though the amount of reduction decreases, and at 20% or more, the silencing effect becomes the largest. Therefore, it is understood that the aperture ratio is more preferably 20% or more.
  • the upper limit of the aperture ratio is better for the muffling effect as the aperture ratio is higher, but if it is too large, the rigidity of the first surface plate is reduced, so 90% or less is preferable and 70% or less is more preferable. And 50% or less at which the muffling effect is saturated is most preferable.
  • the calculation method is as follows. Assuming that the acoustic impedance of the resonant structure 28 is Zh, it can be expressed by the following equation (2).
  • R is the acoustic resistance in the through hole 18, and was set so that the sound absorption coefficient becomes 99.9% at the time of resonance (the imaginary part is 0).
  • h ′ is the thickness of the first surface plate 16 including the open end correction of the through hole 18. Also, ⁇ is the air density, c is the speed of sound, l is the length of the back space (the thickness of the honeycomb core 12), and ⁇ is the angular frequency.
  • the first term of the imaginary part indicates the inductance of the through hole 18, and the second term indicates the capacitance of the closed space.
  • the inventors also calculated the open area ratio of the through holes 18, the thickness of the honeycomb core 12, and the thickness of the first surface plate 16 from the calculation results of the graphs shown in FIG. 6B and 16 types of graphs shown in FIGS.
  • the desirable relational expression shown to the following inequality (1) with thickness was found out.
  • the thickness of the honeycomb core is l
  • the thickness of the first surface plate is h
  • the aperture ratio of the through hole 18 is ar
  • f 1 (l, h) ⁇ ln (ar) + f 2 (l, h) ⁇ 1.5
  • f 1 (l, h) A 1 (h) ⁇ l 2 + A 2 (h) ⁇ l + 0.24915
  • f 2 (l, h) A 3 (h) ⁇ l 2 + A 4 (h) ⁇ l + 1.804
  • a 1 (h) 19.466 ⁇ ln (h) -0.3038
  • a 2 (h) ⁇ 1.611 ⁇ ln (h) +4.0162
  • a 3 (h) 119.22 ⁇ ln (h) +78.249
  • a 4 (h) -5689.7 ⁇ h + 94.861
  • FIG. 40 to 55 show the reduction amounts obtained by subtracting the noise level in the soundproof structure from the total noise amount (noise level) of pink noise for each of the 16 types of graphs determined above including FIG. 6A. It is each graph of 16 types to express. Among them, FIG. 6B shows a graph shown in FIG. 46 corresponding to FIG. 6A to which a line of calculation indicating the equation of the left side of the inequality (1) is added. 46 and 6B, the thickness l of the honeycomb core 12 is 0.03 m (30 mm), and the thickness h of the first surface plate 16 is 0.001 m (1 mm). From FIG. 46 to FIG. 55 and FIG.
  • the reduction amount of the noise level in the soundproof structure of the present invention largely depends on the thickness l of the honeycomb core 12 and the thickness h of the first surface plate 16 in addition to the aperture ratio ar I understand.
  • the above inequality (1) is a condition under which a silencing effect of 1.5 dB or more is obtained It is understood that it prescribes.
  • the inequality (1) needs to be 1.5 dB or more. The reason is that the noise reduction can be felt by hearing.
  • the inequality (1) is preferably 1.7 dB or more, more preferably 2 dB or more.
  • 1 dB is the minimum unit of dB, and represents that the total energy of noise is reduced by 10%. Also, 1.5 dB represents that the total energy of noise is reduced by 1.4%. Also, 1.7 dB represents that the total energy of the noise is reduced by 1.5%. Further, 2 dB represents that the total energy of noise is reduced by 1.6%, and 3 dB represents that the total energy of noise is reduced to half.
  • the sound absorber 22 can be supported on one surface of the first face plate 16 so that the distance between the first face plate 16 and the second face plate 20 can be maintained constant.
  • the material is not particularly limited as long as it can hold the honeycomb core 12, and the same material as the honeycomb core 12 can be used.
  • the material of the first surface plate 16 may support the sound absorber 22 and may form an air column resonance structure with the honeycomb core 12 and the second surface plate 20 behind the through holes 18 of the first surface plate 16. . Therefore, the first front plate 16 is preferably made of paper, metal or resin.
  • the second surface plate 20 is spaced apart from the first surface plate 16 on the other surface of the honeycomb core 12 (the lower surface in FIG. 1; that is, the surface opposite to the side on which the sound absorber 22 is provided). Be done.
  • the second surface plate 20 is for sealing the other side (lower side in FIG. 1) of the plurality of openings 14 of the honeycomb core 12, and holds the honeycomb core 12 between the second surface plate 20 and the first surface plate 16. It is for.
  • the thickness of the second surface plate 20 is not particularly limited as long as it can support the honeycomb core 12 between the first surface plate 16 and the second surface plate 20.
  • the thickness is preferably 0.001 mm (1 ⁇ m) to 5 mm.
  • planar shape and the size (planar size) of the second surface plate 20 are not particularly limited, depending on the planar shape, the size, etc. of the first surface plate 16 or the sound absorber 22 and the honeycomb core 12. It may be determined appropriately and may be selected.
  • the material of the second front plate 20 is not particularly limited as long as the honeycomb core 12 can be held between the first front plate 16 and the second front plate 16, and the same material as the first front plate 16 can be used.
  • a material of the second surface plate 20 various metals such as paper, aluminum and iron, and various resin materials such as polyethylene terephthalate (PET) can be used.
  • PET polyethylene terephthalate
  • the second front plate 20 is preferably made of paper, metal or resin. Further, as long as the second surface plate 20 can sandwich the honeycomb core 12 with the first surface plate 16, the second surface plate 20 may be a component member or wall of various devices on which the soundproof structure is installed.
  • the surface of the honeycomb core 12 opposite to the surface on which the first surface plate 16 is disposed may be used as the second surface plate 20 by arranging the frame so as to be in contact with the wall.
  • the sound absorber 22, the first surface plate 16, the honeycomb core 12, and the second surface plate 20 are separate members, the sound absorber 22, the first surface plate 16, the honeycomb core 12, and the second surface plate At least two of 20 may be integrated.
  • the first surface plate 16 and the honeycomb core 12 may be integrated, or the honeycomb core 12 and the second surface plate 20 may be integrated.
  • the sound absorber 22, the first surface plate 16 and the honeycomb core 12 may be integrated, or the first surface plate 16, the honeycomb core 12 and the second surface plate 20 may be integrated. It may be a configuration.
  • the sound absorber 22, the first front plate 16, the honeycomb core 12, and the second front plate 20 may be integrated.
  • a member or the like in which at least two of the sound absorber 22, the first surface plate 16, the honeycomb core 12, and the second surface plate 20 are integrated can be manufactured, for example, by a 3D printer. Further, a member in which the sound absorber 22, the first surface plate 16, the honeycomb core 12 and the second surface plate 20 are integrated is, for example, a member forming the sound absorber 22, the first surface plate 16, the honeycomb core 12 and the first After integral molding of the two-face plate 20 with a 3D printer, as will be described later, it can be manufactured by forming the fine through holes 24 in a member forming the sound absorber 22 with a laser.
  • the 1st surface board 16, the honeycomb core 12, and the 2nd surface board 20 are paper, it is preferable that they are cloths, such as woven cloth or knitting cloth, of the sound-absorbing body 22 mentioned later.
  • cloths such as woven cloth or knitting cloth.
  • the honeycomb portion formed of the first front plate 16, the honeycomb core 12, and the second front plate 20 is a combustible paper, it is preferable that the woven fabric or the mesh fabric is also combustible.
  • the effect of using a cloth such as woven cloth or net cloth as a sound absorbing material is light weight, low cost, and designability. It is waterproof, water repellent, flammable, or recyclable.
  • the sound absorber 22 is disposed in contact with one of the main surfaces (the lower surface in FIG. 1) of the first surface plate 16.
  • the sound absorber 22 is preferably a porous material.
  • the sound absorbing body 22 may be, for example, a fine through hole plate 26 having a plurality of fine through holes 24 penetrating in the thickness direction like the soundproof structure 10 shown in FIG. 1 or the soundproof structure 11 shown in FIG.
  • the nonwoven fabric 27 may be used.
  • woven cloth, knitted cloth, fibers such as felt, porous materials such as urethane, and the like can be mentioned.
  • the sound absorber 22 by using a fiber of a sub-nano order fiber diameter as the sound absorber 22, it is preferable because a high sound absorption effect can be obtained compared to the conventional non-woven fabric.
  • the sound absorber 22 specifically, as a non-woven fabric, Thinsulate (trademark, manufactured by 3M), sound absorbing felt, metal fiber (Poal (manufactured by Unix)), glass wool, rock wool, porous material: urethane, And gypsum board.
  • woven cloths include non-combustible cloths (manufactured by ISTOFLON IST Co., Ltd.) and polyester cloths (JEDI SCREEN 3000AT, 4000NT, Hiraoka Textiles Inc.).
  • the sound absorber 22 is disposed only on one surface (upper surface in FIG. 1) of the first surface plate 16.
  • the sound absorber 22 is constituted by a fine through hole plate 26 having a plurality of fine through holes 24 penetrating in the thickness direction.
  • the fine through hole plate 26 when the average diameter is 1.0 mm or less, the frictional resistance of the fine through hole 24 increases, which is preferable as the thin sound absorber 22. Further, a fine through hole of 250 ⁇ m or less is more preferable because a wider band sound absorption characteristic can be obtained.
  • the average diameter of the fine through holes 24 is also preferably 1.0 ⁇ m or more. That is, the plurality of fine through holes 24 of the fine through hole plate 26 preferably have an average diameter of 1.0 ⁇ m to 250 ⁇ m.
  • the average diameter of the fine through holes 24 is preferably 1.0 ⁇ m to 250 ⁇ m is that if the average diameter is less than 1.0 ⁇ m, the acoustic resistance is too large and the sound absorption characteristics are deteriorated. This is because when it exceeds 250 ⁇ m, the inductance of the fine through holes 24 increases and the band narrows.
  • the fine through holes 24 may or may not be regularly perforated in the fine through hole plate 26 in shape, size (diameter) and arrangement.
  • the diameter of the fine through holes 24 can be defined in the same manner as the diameter of the through holes 18.
  • the sound absorbing body 22 has a plurality of fine through holes 24 penetrating in the thickness direction, even if it is a film-like (film-like) fine through-hole plate 26, a fibrous fine through-hole plate 26 It may be In the case of the fibrous fine through hole plate 26, the space between the fibers can be regarded as the fine through hole 24.
  • the fine through-hole plate 26 may or may not have regularity in the fine through-hole plate 24, and as described above, it may be a fiber itself, and it may be a woven or non-woven fabric having various weaves good.
  • the sound absorbing body 22 composed of the fine through hole plate 26 is more preferable because a high sound absorbing effect can be obtained even in a thin state.
  • the shape of the fine through hole 24 is planar and circular, it is not particularly limited in the present invention.
  • the shape of the micro through hole 24 may be a rectangle, a rhombus, or another quadrilateral such as a parallelogram, a regular triangle such as an equilateral triangle, an isosceles triangle or a right triangle, a regular pentagon, or a regular hexagon. It may be a polygon including or oval or the like, or may be indeterminate.
  • the soundproof structure 10 of the present invention comprises a sound absorber 22 comprising fine through-hole plates 26 and an air column formed by the honeycomb core 12 and the second surface plate 20 behind the first face plate 16 having the through holes 18.
  • the resonant structure improves the sound absorption performance, and has the effect of broadening the sound absorption frequency.
  • the average diameter of the plurality of fine through holes 24 formed in the fine through hole plate 26 is 0.1 ⁇ m or more and less than 100 ⁇ m, and the average aperture ratio of the fine through holes 24 is as follows.
  • the fine through-hole plate 26 alone is independent even without the air column resonance structure formed by the first surface plate 16 having the through holes 18, the honeycomb core 12, and the second surface plate 20. Therefore, it can function as a soundproof structure which produces a high sound absorption effect.
  • the fine through hole plate 26 of the present invention has fine through holes 24 with an average diameter of 0.1 ⁇ m or more and less than 100 ⁇ m with an average aperture ratio in the above range, so that fine through holes 24 when sound passes through the fine through holes 24 The sound is absorbed by the friction between the inner wall surface 24 and the air. That is, the fine through hole plate 26 is sound absorption by resonance with the closed space of the air layer behind the resonance structure formed by the first surface plate 16 having the through holes 18, the honeycomb core 12, and the second surface plate 20; It can be combined with sound absorption by a mechanism that is not resonance.
  • the sound absorption in the fine through hole plate 26 is based on the principle of Helmholtz resonance (resonance) in which the connection between the air layer in the fine through hole 24 and the air layer in the closed space functions as a mass spring to cause resonance and sound absorption. Is not used.
  • the sound absorption by the fine through hole plate 26 of the soundproof structure 10 of the present invention is a sound absorption effect by air column resonance in the air layer in the closed space, and the inner wall surface of the fine through hole 24 and the air when sound passes through the fine through hole 24 Together with the sound absorption effect.
  • the sound absorbing mechanism of the sound absorbing body 22 itself comprising the fine through hole plate 26 is to the thermal energy of the energy of the sound due to the friction between the inner wall surface of the fine through hole 24 and the air when the sound passes through the fine through hole 24 Estimated to be a change in This mechanism is different from the mechanism by resonance because it is caused by the fine size of the fine through holes 24.
  • a path that passes directly as a sound in air by the fine through holes 24 has a much smaller acoustic impedance than a path that is once converted to film vibration and then emitted again as a sound. Therefore, the sound is more likely to pass through the path of the fine through holes 24 than the membrane vibration.
  • the sound When passing through the fine through hole portion, the sound is concentrated and passed from the entire wide area on the fine through hole plate 26 to the narrow area of the fine through hole 24.
  • the local velocity is extremely increased by the collection of sounds in the minute through holes 24.
  • the friction As the friction is correlated with the speed, the friction increases in the fine through holes 24 and is converted to heat.
  • the average diameter of the fine through holes 24 is small, the ratio of the edge length of the fine through holes 24 to the opening area is large, so that the friction generated at the edges and / or the inner wall of the fine through holes 24 is increased. It is believed that By increasing the friction when passing through the fine through holes 24, it is possible to convert sound energy into heat energy and absorb sound.
  • an optimum ratio exists to the average aperture ratio of the fine through holes 24.
  • the average diameter is relatively large such as about 50 ⁇ m or more
  • the smaller the average aperture ratio the higher the absorptivity.
  • the average aperture ratio is large, the sound passes through each of the many fine through holes 24, whereas when the average aperture ratio is small, the number of the fine through holes 24 decreases, so one fine The sound passing through the through hole 24 increases, and the local velocity of air passing through the fine through hole 24 is further increased, and the friction generated at the edge and the inner wall surface of the fine through hole 24 can be further increased.
  • the fine through hole plate 26 has the fine through holes 24, even if a liquid such as water adheres to the fine through hole plate 26, the surface tension prevents water from avoiding the fine through holes 24. Since the fine through holes 24 are not closed, the sound absorption performance is unlikely to be reduced. Further, since the fine through hole plate 26 is a thin layered film, it can be curved according to the place to be arranged.
  • the sound absorbing mechanism of the fine through hole plate 26 alone functions only with the fine through hole plate 26 and does not require a closed space behind the fine through hole plate 26. However, even if a closed space such as a room wall with respect to the window is configured behind the minute through hole plate 26, the same function can be obtained.
  • the surface on the sound incident side of the fine through-hole plate 26 is the surface, the opposite side is the back, and the space on the back side of the fine through-hole plate 26 is the space behind.
  • the incident direction of sound when a noise source such as a speaker or machine noise is clear, for example, the direction of itself can be determined as the incident direction.
  • sound source phase information and particle velocity can be measured simultaneously with sound pressure amplitude information using a microphone array, beam forming, or PU probe.
  • Direction can be determined.
  • Ono Sokki's three-dimensional intensity probe MI-6420, Microflown's PU probe (sound pressure-particle velocity probe), Breuer &Keller's microphone array system, etc. only the sound pressure is strong. Not just the position can be determined.
  • the upper limit value of the average diameter of the fine through holes 24 is less than 100 ⁇ m, preferably 80 ⁇ m or less, more preferably 70 ⁇ m or less, most preferably 50 ⁇ m or less, most preferably 30 ⁇ m or less. This is because the smaller the average diameter of the fine through holes 24, the larger the ratio of the length of the edge of the fine through holes 24 contributing to the friction to the opening area of the fine through holes 24, and the friction It is because it becomes easy to occur. Further, the lower limit value of the average diameter is preferably 0.5 ⁇ m or more, more preferably 1 ⁇ m or more, and still more preferably 2 ⁇ m or more. If the average diameter is too small, the viscous resistance at the time of passing through the fine through holes 24 is too high to pass sound sufficiently, so that even if the aperture ratio is increased, sufficient sound absorbing effect can not be obtained.
  • the average opening rate rho of the fine through holes 24 is the average opening rate rho of the fine through holes 24.
  • Is a range greater than 0 and less than 1 and having rho_center (2 + 0.25 ⁇ t) ⁇ phi ⁇ 1.6 as the lower limit, with rho_center ⁇ (0.052 ⁇ (phi / 30) ⁇ 2 ) as the lower limit, rho_center + (0.795) It is in the range which makes x (phi / 30) -2 ) the upper limit.
  • the average aperture ratio rho is preferably in the range of rho_center ⁇ 0.050 ⁇ (phi / 30) ⁇ 2 or more, rho_center + 0.505 ⁇ (phi / 30) ⁇ 2 or less, and rho_center ⁇ 0.048 ⁇ (phi / 30) ⁇ 2 or more
  • the range of (rho_center ⁇ 0.24 ⁇ (phi / 10) ⁇ 2 ) or more and (rho_center + 0.57 ⁇ (phi / 10) ⁇ 2 ) or less is particularly preferable, and (rho_center ⁇ 0.185 ⁇ (phi / 10) ⁇ 2 ) or more,
  • the average diameter of the plurality of fine through holes 24 formed in the fine through hole plate 26 which is the sound absorber 22 is 0.1 ⁇ m or more and less than 100 ⁇ m, the fine through holes 24 are formed.
  • Setting the average aperture ratio rho in the above-mentioned range is to optimize the sound absorption coefficient (absorptivity when sound passes through the sound absorber 22) of the sound absorber 22 alone of the present invention. As described above, optimizing the sound absorption coefficient of the sound absorber 22 alone (the absorptivity when sound passes through the sound absorber 22) results in obtaining high acoustic resistance in the sound absorber 22.
  • the sound absorption of the minute through holes 24 themselves and the resonance in the air column resonance structure formed by the first surface plate 16, the honeycomb core 12 and the second surface plate 20 It is possible to add a large acoustic resistance value that is optimum for obtaining wide band characteristics.
  • the average aperture ratio rho which is a parameter for optimizing the sound absorption coefficient of the fine through hole plate 26 alone (absorptivity when sound passes through the fine through hole plate 26), provides the optimum acoustic resistance in air column resonance. Equal to the parameter.
  • the mean diameter of the fine through holes 24 is 200 times the surface of the fine through hole plate 26 using a high resolution scanning electron microscope (SEM) from the surface side of the fine through hole plate 26 (sound absorber 22)
  • SEM scanning electron microscope
  • 20 fine through holes 24 whose circumferences are annularly continuous are extracted, their diameters are read, and their average value is calculated as an average diameter. If the number of micro through holes 24 is less than 20 in one SEM photograph, SEM photographs are taken at another position around the periphery and counted until the total number reaches 20.
  • the diameter measured the area of the part of the fine through-hole 24, respectively, and evaluated using the diameter (circle equivalent diameter) when replacing with the circle used as the same area.
  • the shape of the opening of the fine through hole 24 is not limited to a substantially circular shape, when the shape of the opening is non-circular, the diameter of the circle having the same area was evaluated. Therefore, for example, even in the case of a fine through hole having a shape in which two or more fine through holes are integrated, this is regarded as one fine through hole 24 and the circle equivalent diameter of the fine through hole 24 is the diameter.
  • the circle equivalent diameter, the aperture ratio and the like can all be calculated by Analyze Particles using “Image J” (https://imagej.nih.gov/ij/).
  • the average aperture ratio is obtained by photographing the surface of the sound absorber 22 at a magnification of 200 times from directly above using a high resolution scanning electron microscope (SEM), and the field of view of 30 mm ⁇ 30 mm of the obtained SEM photograph (5 places) Of the fine through holes 24 and the non-fine through holes are binarized with image analysis software etc., and the ratio from the total of the open areas of the fine through holes 24 and the area of the field of view (geometrical area) It calculates from (opening area / geometrical area), and calculates the average value in each visual field (five places) as an average aperture ratio.
  • SEM scanning electron microscope
  • the through holes 18 of the first surface plate 16 By the way, if the hole diameter of the plurality of through holes 18 of the first surface plate 16 is large and regularly arranged, the through holes 18 will be visually recognized. Therefore, the through hole 18 is visually recognized if it is actually used as it is on a wall, a vehicle ceiling, a floor, etc., and there is a problem that a design and a texture are greatly disturbed. For this reason, in the present invention, even if the hole diameters of the plurality of through holes 18 of the first surface plate 16 are large and regularly arranged, one main surface of the first surface plate 16 (viewing side The micro through hole plate 26 having the plurality of micro through holes 24 is attached and disposed on the surface) so that the plurality of through holes 18 of the first front plate 16 are not visually recognized.
  • the energy of the sound when sound passes through the fine through holes 24 of the fine through hole plate 26, the energy of the sound is converted into thermal energy by the friction between the inner wall surface of the fine through holes 24 and air.
  • Improve the efficiency of thereby, the efficiency of sound absorption by the air column resonance structure consisting of the honeycomb core 12 behind the through hole 18 of the first surface plate 16 and the second surface plate 20 is improved, and the soundproofing efficiency of the soundproof structure 10 of the present invention is lowered. To prevent.
  • the plurality of fine through holes 24 may be one having a diameter of 1 ⁇ m to 250 ⁇ m, and may have one type of fine through holes 24 or two or more types of fine through holes 24. It may be one. From the viewpoint of productivity, the viewpoint of durability, etc., it is preferable to be composed of fine through holes 24 of two or more diameters. As for the productivity, if the variation in diameter is allowed from the viewpoint of performing a large amount of etching processing, the productivity is improved.
  • the size of dust and dirt varies depending on the environment, so if it is a fine through-hole with a single diameter, all fine through-holes when the size of the main dust approximately matches the fine through-hole Will affect the By providing micro through holes of a plurality of different diameters, the device can be applied in various environments.
  • the dust passing through the outermost surface of the fine through hole is caught in the small diameter part of the inside, compared to the fact that the dust tends to remain as it is.
  • the shape with the largest diameter at the above functions advantageously in the suppression of dust clogging.
  • the largest diameter is "largest diameter> dust size> other surface"
  • the inner wall surface of the fine through holes is preferably roughened.
  • the surface roughness Ra of the inner wall surface of the fine through hole is preferably 0.1 ⁇ m or more, more preferably 0.1 ⁇ m to 10.0 ⁇ m, and 0.2 ⁇ m or more and 1.0 ⁇ m or less Is more preferred.
  • the surface roughness Ra can be measured by measuring the inside of the fine through holes with an AFM (Atomic Force Microscope).
  • AFM Anatomic Force Microscope
  • SPA300 manufactured by Hitachi High-Tech Science Co., Ltd.
  • the cantilever can be measured in DFM (Dynamic Force Mode) mode using OMCL-AC200TS. Since the surface roughness of the inner wall surface of the fine through hole is about several microns, it is preferable to use AFM in terms of having a measurement range and accuracy of several microns.
  • the average particle diameter of the convex portion is calculated by regarding each of the convex portions of the unevenness in the fine through hole as particles.
  • an SEM image field of view of about 1 mm ⁇ 1 mm
  • yen which becomes the same area as each area is calculated
  • the average particle diameter of the convex portion is preferably 0.1 ⁇ m or more and 10.0 ⁇ m or less, and more preferably 0.15 ⁇ m or more and 5.0 ⁇ m or less.
  • the ventilation flow resistance of the sound absorber 22 is 10 to 50000 Rayls (Pa ⁇ s / m or N ⁇ s / m 3 , Rayls in the present invention). Is preferably used, more preferably 50 to 10000 Rayls, and most preferably 100 to 2000 Rayls.
  • the sound absorption coefficient (viscous resistance) optimum for the first surface plate 16 having a small diameter of the through hole 18 and a small aperture ratio can be obtained at 10 Rays or more, but there is almost no resistance if it is smaller. On the other hand, when it exceeds 50000 Rayls, the resistance is too large and reflection mainly occurs to reduce the sound absorption effect.
  • the total throughflow resistance of the throughflow resistance R1 of the through hole 18 of the first surface plate 16 and the throughflow resistance R2 of the sound absorber 22 is 12 Rayls or more, and preferably 16700 Rayls or less. With such a total air flow resistance, a sound absorption effect of 10% or more can be obtained at the resonance frequency.
  • the total ventilation flow resistance described above is 75 Rayls or more, more preferably 2570 Rayls or less, still more preferably 150 Rayls or more, and still more preferably 1150 Rayls or less.
  • a more preferable range of the total vent flow resistance described above is a value at which a sound absorption effect of 50% or more is obtained at the resonance frequency, and a still more preferable after range of the above total vent flow resistance is 80% or more at the resonance frequency.
  • the condition under which the sound absorption effect of As shown in FIG. 8, when the total air flow resistance as described above becomes larger than 300 Rayls, the increase in the sound absorption coefficient is saturated, which is most preferable. That is, if it exceeds 300 Rayls, the robustness is high (the flow resistance is insensitive), and a high sound absorption effect can be obtained.
  • the upper limit is preferably 16700 Rayls or less, and most preferably 1150 Rayls or less.
  • the ventilation flow resistance R1 of the portion of the through hole 18 of the first surface plate 16 is expressed by the following formula (4).
  • ⁇ air density
  • c sound velocity
  • ⁇ viscous drag of air
  • ⁇ angular frequency
  • t thickness of surface plate
  • a radius of hole
  • design is performed using an acoustic module of COMSOLver 5.1 (COMSOL Inc) which is analysis software of finite element method.
  • the local velocity indicates the local moving velocity of the medium that mediates the sound wave. From this, it was assumed that particles were vibrating in the penetration direction of the fine through holes, and the movement distance was determined. Since the sound is vibrating, the distance amplitude is a distance that can be moved within a half cycle. At 2500 Hz, since one cycle is 1/2500 seconds, half of the time can be in the same direction.
  • the maximum travel distance (acoustic travel distance) in the sound wave half cycle determined from the local velocity is 10 ⁇ m at 94 dB and 0.2 ⁇ m at 60 dB. Therefore, the friction is increased by having the surface roughness about this acoustic movement distance, so the range of the surface roughness Ra described above and the range of the average particle diameter of the convex portion are preferable.
  • the thickness of the fine through hole plate 26 which is the sound absorbing body 22 is not limited. However, since the friction energy received when the sound passes through the fine through hole 24 increases with the thickness, the sound absorbing performance is further improved. Conceivable. Moreover, when it is extremely thin, it is difficult to handle it and it is easy to break it. On the other hand, it is preferable that the miniaturization, the air permeability and the light transmission be thin. In the case of using etching or the like for the method of forming the fine through holes 24, the longer the thickness, the longer the preparation time, and the thinner is desirable from the viewpoint of productivity.
  • the thickness of the sound absorber 22 is preferably 50 mm or less, more preferably 25 mm or less, more preferably 20 mm or less, still more preferably 10 mm or less, still more preferably 5 mm or less, still more preferably 2 mm or less, 1 mm or less Is most preferred.
  • the sound absorbing body 22 is susceptible to mechanical damage, so it is preferably 0.1 ⁇ m or more, more preferably 1.0 ⁇ m or more, and 10 ⁇ m or more.
  • Examples of the sound absorber 22 having a thickness of 1 mm or less include sheets such as woven cloth and knitted cloth, and membrane members.
  • the planar shape and the size (planar size) of the sound absorber 22 (the fine through hole plate 26) are not particularly limited, and may be appropriately determined according to the planar shape, the size, and the like of the first surface plate 16. And you may choose.
  • the sound absorbing body 22 is a film-like (film-like) fine through hole plate 26 having a plurality of fine through holes 24
  • the material of such a fine through hole plate 26 is not particularly limited, and the same material as the material of the honeycomb core 12 can be used.
  • the material of the sound absorber 22 is, for example, aluminum, titanium, nickel, permalloy, 42 alloy, kovar, nichrome, copper, beryllium, phosphor bronze, brass, nickel, tin, zinc, iron, tantalum, niobium, molybdenum, zirconium , Metals such as gold, silver, platinum, palladium, steel, tungsten, lead, stainless steel, and iridium; alloy materials based on those metals; PET (polyethylene terephthalate), TAC (triacetyl cellulose), polyvinylidene chloride, polyethylene, Polyvinyl chloride, polymethylbenzene, COP (cycloolefin polymer), polycarbonate, zeonoa, PEN (polyethylene naphthalate), polypropylene, and polyimide, ABS resin (acrylonitrile (Acrylonitrile), butadiene (Butadiene), styre (Styrene) copoly
  • the material of the sound absorber 22 is preferably a flame retardant material particularly when the first surface plate 16, the second surface plate 20, and the honeycomb core 12 are made of a flammable material such as paper.
  • the flame retardant material is more preferably a metal material. That is, it is more preferable to use a metal material from the viewpoints of high flame retardancy, high Young's modulus, low vibration even when the thickness is thin, and the effect of sound absorption by friction in fine through holes is easily obtained.
  • copper, nickel, stainless steel, titanium and aluminum are more preferable from the viewpoint of cost and availability.
  • the average diameter of the fine through holes may be adjusted to a smaller range by metal plating at least on the inner surface of the fine through holes.
  • a conductive material such as a metal material which is not electrically charged as a material of the sound absorber 22
  • fine dust, dust and the like are not attracted to the film by static electricity, and the fine through hole plate 26 It is possible to suppress that the sound absorption performance is reduced due to dust, dirt and the like being clogged in the through hole 24.
  • heat resistance can be made high by using a metal material as a material of a fine through-hole board.
  • ozone resistance can be enhanced.
  • an electromagnetic wave can be shielded.
  • the metal material has a large reflectance to radiant heat by far infrared rays
  • the metal material is used as a material of the fine through-hole plate to also function as a heat insulating material for preventing heat transfer by the radiant heat.
  • the fine through hole plate functions as a reflective film because the diameter of the fine through holes is small.
  • a structure in which a plurality of fine through holes are opened in metal is known to function as a high pass filter of frequency. For example, a window with a metal mesh of a microwave oven has a property of shielding visible light that is high frequency while passing microwaves used in the microwave oven.
  • Radiant heat is a heat transfer mechanism in which far infrared rays are emitted from an object in accordance with the object temperature and transmitted to another object.
  • the average diameter of the fine through holes formed in the fine through hole plate is preferably 20 ⁇ m or less.
  • a resin material or glass material that can be made transparent can be used.
  • a PET film has relatively high Young's modulus among resin materials, is easily available, and has high transparency, so that fine through holes can be formed to provide a suitable soundproof structure.
  • the micro through-hole plate is appropriately subjected to surface treatment (plating treatment, oxide film treatment, surface coating (fluorine, ceramic), etc.) according to the material to improve the durability of the micro through-hole plate. be able to.
  • an oxide film can be formed on the surface by performing an alumite treatment (anodic oxidation treatment) or a boehmite treatment. By forming an oxide film on the surface, corrosion resistance, abrasion resistance, abrasion resistance and the like can be improved. Further, by adjusting the treatment time and adjusting the thickness of the oxide film, it is possible to adjust the color tone by optical interference.
  • coloring, decoration, decoration, design, etc. can be given to a fine through-hole board.
  • an appropriate method may be selected depending on the material of the fine through hole plate and the state of surface treatment. For example, printing using an inkjet method can be used.
  • coloring with high durability can be performed by performing a color alumite process.
  • the color alumite treatment is a treatment in which the surface is subjected to alumite treatment, then impregnated with a dye, and then the surface is sealed. By this, it can be set as the fine through-hole board with high designability, such as the presence or absence and color of metallic luster.
  • the anodized film is formed only on the aluminum portion, so that the dye covers the fine through holes and the decoration is performed without reducing the sound absorption characteristics. It can be performed.
  • various colors and designs can be added.
  • the fine through-hole plate may be a woven fabric, and a fiber itself such as a knitted fabric, or a fibrous membrane such as a non-woven fabric.
  • fibrous membranes the spaces between the fibers can be regarded as through holes.
  • the fibers themselves are in the form of a film, the fibers are irregularly overlapped, and in the case of a non-woven fabric, the fibers are irregularly woven, so the fibers are not parallel or orthogonal to each other, Through holes are formed in the space surrounded by the fibers. Therefore, the mean diameter and the mean open area ratio of the fine through holes are determined by the fiber diameter and the density.
  • a fine through-hole board is a fibrous film
  • 100 micrometers or less are more preferable.
  • the fiber diameter of the fibrous film is usually about several tens of ⁇ m. Therefore, many yarns will not be laminated
  • the characteristics of such woven fabrics and fibrous films such as knitted fabrics include waterproofness or water repellency as described above, and patterns, images, photographs, etc. are drawn for design. In addition to this, it also includes lightweight, low cost, flammable, or recyclability.
  • the material of the fibrous film includes aramid fiber, glass fiber, cellulose fiber, nylon fiber, vinylon fiber, polyester fiber, polyethylene fiber, polypropylene fiber, polyolefin fiber, rayon fiber, low density polyethylene resin fiber, ethylene vinyl acetate resin fiber , Fiber made of resin material such as synthetic rubber fiber, copolyamide resin fiber, copolyester resin fiber, etc .; paper (tissue paper, Japanese paper etc.); SUS fiber (stainless fiber sheet manufactured by Yodogawa Paper Co., Ltd. "Tomy Fileck” Fibers made of a metal material such as “SS” etc.); fibers of a carbon material, fibers of a carbon-containing material, and the like.
  • the absorption characteristic in the present invention is generated when sound passes through the fine through holes, the acoustic characteristics hardly change even if the material of the fibrous member changes.
  • the material can be selected freely.
  • it can also select according to characteristics other than an acoustic characteristic. For example, if heat resistance is required, a metal material can be selected, and if weight reduction is required, a plastic material can be selected.
  • the sound absorber 22 and the first front plate 16 may be disposed in contact with each other, but it is preferable that they be adhered and fixed. By bonding and fixing the sound absorber 22 and the first surface plate 16, the rigidity of the sound absorber 22 can be made higher, and the resonance vibration frequency can be made higher.
  • the adhesive used to bond and fix the sound absorber 22 and the first surface plate 16 may be selected according to the material of the sound absorber 22 and the material of the first surface plate 16 or the like.
  • epoxy-based adhesive Aldite (registered trademark) (manufactured by Nichiban Co., Ltd.) and the like
  • cyanoacrylate-based adhesive Aron Alpha (registered trademark) (manufactured by Toagosei Co., Ltd. and the like)
  • acrylic A system adhesive etc. can be mentioned.
  • the sound absorber 22 have a deodorizing function.
  • a deodorizing function in the case where the sound absorbing body 22 is a fibrous film, a fine through hole plate, or a porous material, it is sufficient to impregnate the deodorant in each of the fibers.
  • a deodorant a well-known deodorant can be used.
  • Deodorants include, for example, odor-free air and cloth deodorant mist made by Kobayashi Pharmaceutical Co., Ltd., Orbuse's Revenge Natural Caribbean Rush Up Spray (CR-TN012), Goodwill Biol Will Clear Spray E483184H) and the like.
  • the air column resonance structure can be configured by providing the first surface plate 16, the honeycomb core 12, and the second surface plate 20, and The column resonance structure can reduce the resonance center frequency. Further, in the present invention, the rigidity of the fine through hole plate 26 and the first surface plate 16 can be further enhanced by the honeycomb core 12 and the second surface plate 20. In the present invention, it is preferable that the average diameter is 1 ⁇ m to 250 ⁇ m, and the fine through hole plate 26 having the fine through hole structure having the fine through holes 24 is a through hole of the first surface plate 16 of the air column resonance structure.
  • the through hole 18 of the air column resonance structure can be obscured, the appearance of the exterior can be enhanced, and a wide band sound absorption can be performed.
  • the fine through hole plate 26 with metal, the first surface plate 16, the honeycomb core 12, and the second surface plate 20 constituting the air column resonance structure are made of a flammable material such as synthetic resin or paper. If so, the fire resistance of the structure can be increased. That is, although the soundproof structure according to the present invention uses the air column resonance structure, it can not only improve the appearance but also enhance the sound absorption effect, compared with other sound absorption structures. There is a wide band and high sound absorption effect.
  • the soundproof structure of the present invention can be used as a soundproofing member as described below in addition to the above.
  • Soundproofing materials for building materials Soundproofing materials used for building materials
  • Soundproofing members for air conditioning equipment Soundproofing members installed in ventilation openings and air conditioning ducts to prevent external noise
  • Soundproof member for external opening A soundproof member installed in the window of a room to prevent noise from indoor or outdoor
  • Soundproofing material for ceiling A soundproofing material installed on the ceiling of the room to control the sound in the room
  • Floor soundproofing members Soundproofing members installed on the floor that control the sound in the room
  • Soundproofing members for internal openings Soundproofing members installed on indoor doors or bran to prevent noise from each room
  • Soundproofing material for toilets Installed in the toilet or in the door (outdoor), a soundproofing material to prevent noise from the toilet
  • Soundproofing material for balconies A soundproofing material that is installed on a balcony and prevents noise from
  • Interior adjustment members soundproof members for controlling the sound of a room
  • Simple soundproof room member A soundproof member that can be easily assembled and moved easily Soundproof room for pets: A soundproofing unit that encloses the pet room and prevents noise.
  • Amusement facilities Soundproof members installed in game centers, sports centers, concert halls, movie theaters, etc.
  • Soundproofing members for temporary construction enclosures Soundproofing members that cover the construction site and prevent noise from leaking around
  • Soundproofing members for tunnels Soundproofing members installed in a tunnel to prevent noise leaking to the inside and the outside of the tunnel can be mentioned.
  • the soundproof structure of the first embodiment of the present invention is basically configured as described above.
  • the soundproof structure according to the first embodiment of the present invention can be used as it is, for example, in building applications such as inside or outside of buildings, other structures, transportation applications, and logistics applications, but the present invention is limited thereto Instead, a soundproof enclosure using two or more soundproof structures may be used, a soundproof box using a soundproof structure may be used, or a soundproof box using a soundproof enclosure may be used.
  • FIGS. 9A and 9B are a cross-sectional view and a perspective view schematically showing an example of a soundproof box according to a second embodiment of the present invention.
  • the soundproof box 30 shown in FIGS. 9A and 9B uses five of the soundproof structures 10 shown in FIGS.
  • the soundproof box 30 according to the second embodiment of the present invention is a soundproof box enclosed by the soundproof structure 10 according to the first embodiment of the present invention. Therefore, the honeycomb core 12 includes two first and second face plates. By sandwiching by 16 and 20, a high sound absorbing effect can be obtained by the sound absorbing body 22 by disposing the first face plate 16 having the through holes 18 with high rigidity and the inside of the soundproof box 30.
  • both ends of the sound absorber 22 on the first face plate 16 of the two soundproof structures 10 It adheres and fixes to the side of two soundproofing structures 10 (each side edge of sound absorber 22, first face plate 16, honeycomb core 12 and second face plate 20), and the four sides of the rectangular side face Configure.
  • the four ends of the sound absorber 22 on the first face plate 16 of the remaining soundproof structure 10 are the side surfaces of the four soundproof structures 10 that constitute the four sides of the rectangular solid shown in FIG.
  • the soundproof box 30 can be configured.
  • the soundproof box 30 can be used as a soundproof box for pets such as a kennel, a soundproof box for a device (generator, PC) as a noise source, or a soundproof room for people.
  • the soundproof structure 10 on either side of the soundproof box 30 may be provided with an opening for suction and an opening for exhaustion although not shown. That is, it is preferable that a ventilating port for intake and exhaust be disposed in the soundproof box.
  • the soundproof box 30 mentioned above used the soundproof structure 10 of this invention for the wall of 5 surfaces of a rectangular parallelepiped, this invention is not limited to this, The soundproof structure 10 is used for the walls of 6 surfaces of a rectangular parallelepiped Alternatively, one or more openings (not shown) may be provided in the soundproof structure 10 as an entrance and exit on the wall of one side. Also in this case, in addition to the port, an opening (not shown) for intake and exhaust may be provided.
  • the soundproof box 30 can be used for a pet cabin or the like. Further, by arranging a handle (not shown) on the soundproof box 30, it functions as a portable soundproof box, for example, a pet gauge or the like, which is preferable.
  • the soundproof box 30 described above has a rectangular parallelepiped shape
  • the present invention is not limited to this, and as long as it has a box shape, it may have a cubic shape or any other hexahedron shape.
  • it may be a polyhedron shape such as a tetrahedron shape, a pentahedron shape, or an octahedron shape.
  • the example described above is configured using the soundproof structure of the first embodiment of the present invention on the entire wall of the soundproof box of the second embodiment of the present invention or the entire surface wall except one surface.
  • the present invention is not limited thereto, and if the soundproof structure of the present invention is used for at least one side wall, the wall of the remaining face has any structure, for example, the soundproof structure of a comparative example described later. You may use.
  • one surface may be open, or it may be a state such as a partition consisting of one or two sheets.
  • the present invention is not limited to the use of the soundproof structure of the first embodiment to form the soundproof box of the second embodiment, and a soundproof enclosure using two or more of the soundproof structures of the first embodiment.
  • the structure may be configured.
  • the soundproof surround structure of the present invention is the same as the cross section of the soundproof box 30 shown in FIG. 9A, except that the soundproof structure 10 of the ceiling portion of the soundproof box 30 is removed. It is the structure which consists of the wall of the face. Note that a five or more soundproof structure 10 may be used to form a closed soundproof surrounding structure.
  • a soundproof enclosure using two soundproof structures 10 and a soundproof enclosure using three or more soundproof structures 10 are used as a partition surrounding a noise source with the first surface plate 16 side facing the noise source It can also be done.
  • Such a soundproof surrounding structure can raise a high soundproofing effect by arranging so as to surround a noise source.
  • the soundproof box and the soundproof surrounding structure of the second embodiment of the present invention are basically configured as described above.
  • Examples 1 to 3 The soundproof structure 10 shown in FIG. 1 was used.
  • the surface plate 20 (made by Corepack Nishikawa) was adhesively fixed.
  • an acrylic first surface plate 16 having a thickness of 1.0 mm and having the diameter of the through holes 18 as shown in Table 1 and the aperture ratio as shown in Table 1 was adhered and fixed to the other surface of the honeycomb core 12.
  • a fine through hole plate 26 having a diameter of 25 ⁇ m and an opening ratio of 5% was adhered and fixed to the first surface plate 16 as a sound absorber 22 as a sound absorber 22.
  • the adhesive used for adhesive fixing was Spray Paste 77 (manufactured by 3M).
  • the soundproof structure 10 and the soundproof structure 10 of Example 1 are used except that the first face plate 16 made of acrylic having the diameter of the through hole 18 as shown in Table 1 and the aperture ratio as the soundproof structure of Examples 2 and 3 is used. A similar soundproof construction was made.
  • FIG. 11 shows the normal incidence sound absorption coefficient of the soundproof structure of Examples 1 to 3 and Comparative Examples 1 to 2 by measurement using a self-made acoustic tube.
  • Measurement of acoustic characteristics using a self-made acoustic tube was a measurement by a transfer function method using four microphones in a self-made acrylic acoustic tube. This method is in accordance with "ASTM E2611-09: Standard Test Method for Measurement of Normal Incidence Sound Transmission of Acoustical Materials Based on the Transfer Matrix Method".
  • As the acoustic tube for example, one having the same measurement principle as WinZac manufactured by Nittobo Acoustic Engineering Co., Ltd. was used. Sound transmission losses can be measured in a wide spectral band in this way.
  • the soundproof structure 10 of the present embodiment was disposed at the measurement site of the acoustic pipe, and the measurement of the normal incidence sound absorption coefficient of each soundproof structure was performed in the range of 100 Hz to 4000 Hz.
  • the inner diameter of the acoustic tube is 40 mm and can be sufficiently measured up to 4000 Hz or more.
  • Comparative Example 1 no sound absorber is disposed due to high air frictional resistance at the side wall of a small through hole having a diameter of 1.0 mm and an aperture ratio of 0.6%, but as shown in FIG. The rates are shown at a resonant frequency of 690 Hz. However, in Comparative Example 1, the band exhibiting a high sound absorption coefficient is narrow. In Comparative Example 2 in which the same sound absorber as in Example 1 was arranged in the configuration of Comparative Example 1, as shown in FIG. 11, the sound absorption coefficient of the sound absorption peak at the resonance frequency is lowered. This is because the resistance of the sound absorber is added to the air resistance of a small through hole of 1.0 mm and an opening ratio of 0.6%.
  • the sound absorber 22 is bonded and fixed on the first surface plate 16 having the large through holes 18 with a diameter of 3 mm to 5.5 mm and an aperture ratio of 5.7% to 19%. Therefore, as shown in FIG. 11, as the diameter of the through hole 18 is increased and the aperture ratio is increased, the sound absorption center frequency is increased, the band is expanded, and a high sound absorption coefficient is shown in a wide band. I understand that.
  • FIG. 12 shows the result of the noise level in which 10 to 4000 Hz is added by multiplying the pink noise by the transmittance (1-sound absorption coefficient) obtained from the sound absorption coefficient shown in FIG. From this result, it can be seen that the noise level decreases as the aperture ratio of the through holes 18 of the first front plate 16 increases, as in the simulation calculation. Also, it can be seen that the noise level drops sharply at an aperture ratio of 5%, further drops at 10%, and the slope decreases at 20% or more.
  • the sound absorption coefficient is lowered at a high frequency than the air column resonance frequency, but by disposing the sound absorber 22 inside the air column, it is possible to suppress the decrease in sound absorption coefficient. I know what I can do.
  • the diameter of the through hole 18 of the first surface plate 16 needs to be 1.0 mm or more, and the aperture ratio needs to be 1.0% or more. It is understood that 0. 0% or more is preferable.
  • Example 4 to 6 Comparative Example 3
  • the first through-face plate 16 made of acrylic having the diameter of the through hole 18 as shown in Table 1 and the aperture ratio is used.
  • a soundproof structure similar to that of the soundproof structure 10 of Example 1 was produced except that a thin plate of 10 mm in thickness (manufactured by 3M, PPS-200) was used instead of the hole plate 26 as a non-woven fabric.
  • the fine through-hole plates 26 of the soundproofing structures of Examples 1 to 3 are replaced with a non-woven cloth, for example, PNS-200 manufactured by 3M.
  • the soundproof structure of Comparative Example 3 is obtained by replacing the fine through hole plate 26 of the soundproof structure of Comparative Example 2 with a non-woven cloth as a non-woven fabric, for example, PPS-200 manufactured by 3M.
  • FIG. 13 shows the normal incidence sound absorption coefficients of the soundproof structures of Examples 4 to 6 and Comparative Examples 1 and 3 by measurement using the above-mentioned self-made acoustic tube.
  • Comparative Example 3 as in Comparative Example 1, the sound absorption coefficient of the sound absorption peak at the first resonance frequency is lowered, and the sound absorption coefficient is low around 1000 Hz to 2000 Hz, but a thick sound absorber 22 of about 10 mm. Therefore, it can be seen that the sound absorption characteristics increase in the high frequency region from the second resonance frequency.
  • the fourth to sixth embodiments as in the first to third embodiments, as shown in FIG. 13, the diameter of the through hole 18 is increased and the sound absorption center frequency is increased as the aperture ratio is increased.
  • FIG. 14 shows the result of the noise level in which 10 to 4000 Hz is added by multiplying the pink noise by the transmittance (1-sound absorption coefficient) obtained from the sound absorption coefficient shown in FIG. From these results, it can be seen that the noise level drops sharply at an aperture ratio of 5% or more, as in the case where the minute through hole plate 26 is disposed as the sound absorbers 22 of the first to third embodiments.
  • the soundproofing structure of the present invention has a broad band and high sound absorbing effect as compared with various other sound absorbing structures. From the above results, the effects of the present invention are clear.
  • the sound absorber 22 may be a porous material such as non-woven fabric or urethane, or may be a fine through hole plate 26.
  • the film-like fine through-hole plate is used as the sound absorber 22.
  • a non-woven fabric may be used.
  • the structure may be When the sound absorbers are made of metal, it is preferable because nonflammability increases. Moreover, since a sound absorbing body having such fine through holes can obtain a high sound absorbing effect even in a thin state, it is preferable because a high sound absorbing performance can be obtained without largely increasing the thickness of the soundproof structure. In particular, in the case of constructing a box using this soundproof structure, it is possible to suppress a decrease in internal volume, which is preferable.
  • the first surface plate 16 has a hole diameter smaller than the hole diameter of the through hole 18 in addition to the through hole 18. You may have the small through-hole 19 of the small size which is less than 1.0%.
  • the upper surface of the first surface plate 16 (one side opposite to the honeycomb core 12) is provided with one through hole 18 corresponding to one honeycomb cell of the honeycomb core 12.
  • the minute through hole plate 26 (sound absorber 22) is disposed on the However, when one small through hole 19 is provided corresponding to one honeycomb cell of the honeycomb core 12, the fine through hole plate 26 (sound absorber 22) is not disposed.
  • the through holes 18 of the first face plate 16 do not disturb the air column resonance, that is, do not induce the air column resonance to induce the Helmholtz resonance, and a large hole having an aperture ratio of 1% or more It is.
  • the small through hole 19 is a hole smaller than the hole diameter of the through hole 18 having an aperture ratio of less than 1.0% which induces the Helmholtz resonance and does not induce the air column resonance. Therefore, in the soundproof structure 10A, the small through holes 19 are provided in the portion of the first surface plate 16 corresponding to five honeycomb cells of the seven honeycomb cells of the honeycomb core 12, and the two honeycomb cells are A through hole 18 is provided in the corresponding portion of the first front plate 16.
  • the soundproof structure 10A of the present invention shown in FIG. 15 and FIG. 16 is a hole of the first surface plate 16 which is a perforated plate, a through hole 18 for increasing air hole diameter to induce air column resonance, and a small hole diameter Helmholtz
  • the structure uses the small through hole 19 for inducing resonance in combination, since the small through hole 19 for inducing Helmholtz resonance is provided, the band that can be muffled is narrow, and the low frequency band can be muffled in a wide band. Have an effect.
  • Example 11 to 12 and Comparative Example 11 Here, the soundproofing structure 10A shown in FIGS. 15 and 16 as Example 11 and the soundproofing structure 10B shown in FIGS. 17 and 18 as Example 12 and FIG. 19 and FIG. A soundproof structure 34 shown in 20 was used.
  • An acrylic honeycomb core 12 having a diagonal width of 14 mm and a thickness of 30 mm was bonded and fixed to one honeycomb cell.
  • an acrylic plate having a thickness of 2 mm as the first surface plate 16 is formed on the honeycomb core 12 into two upper and lower honeycomb cells in FIG.
  • through holes 18 having a diameter of 10 mm and an aperture ratio of 53% are opened at its center, and small penetrations having a diameter of 1 mm and an aperture ratio of 0.4% corresponding to the remaining five honeycomb cells
  • the holes 19 were arranged in the open state and fixed by adhesion.
  • the aluminum foil having a thickness of 20 ⁇ m is made 25 ⁇ m in diameter as the sound absorber 22.
  • the openings 25 are respectively opened corresponding to the five honeycomb cells in which the small through holes 19 are opened.
  • FIG. 15 the portion where the fine through hole plate 26A exists is shown by hatching.
  • an acrylic plate having a thickness of 2 mm as the first surface plate 16 is formed on the honeycomb core 12.
  • a through hole 18 having a diameter of 10 mm and an open area ratio of 53% was disposed at the center of the seven honeycomb cells and adhesively fixed at the center thereof.
  • a film-like fine through hole plate 26 opened at a rate of 6.2% was used on the entire surface.
  • an acrylic plate having a thickness of 2 mm as the first surface plate 16 is formed on the honeycomb core 12 as shown in FIGS. In a state in which through holes 18 having a diameter of 1 mm and an aperture ratio of 0.4% were opened at the center corresponding to all seven honeycomb cells.
  • the same adhesive as used in Example 1 was used for adhesive fixing.
  • FIG. 21 shows the normal incidence sound absorption coefficients of Examples 11 to 12 and Comparative Example 11 measured with an acoustic pipe in the same manner as Example 1 described above.
  • Comparative Example 11 no sound absorber is disposed due to high air frictional resistance at the side wall of the small through hole 19 (see FIGS. 19 and 20) having an aperture ratio of 0.4% and 1.0 mm. It shows a high sound absorption coefficient at low frequencies. However, it can be seen that the band showing a high sound absorption coefficient is extremely narrow.
  • Example 11 since the large diameter through holes 18 and the small diameter small through holes 19 are mixed in the first surface plate 16, only the large diameter through holes 18 are shown in Table 1 As compared with the embodiment 12 in which the face plate 16 is perforated, it is understood that although the sound absorption band is narrowed, the low frequency band can be muffled in a wide band.
  • the diameter of the through hole 18 is large and the aperture ratio of the through hole 18 is high, so that it is understood that the sound absorption center frequency is high and the band is wide.
  • Example 21 In Example 21, as in the soundproof structure 10C shown in FIGS. 22 and 23, one honeycomb cell is 12 mm wide and 1 mm thick on a second surface plate 20 (made by Core Pack Nishikawa) made of paper and 1 mm thick.
  • a 30 mm paper honeycomb core 12 (made by Corepack Nishikawa) was adhesively fixed.
  • Kraft paper having a thickness of 1 mm as the first surface plate 16 is formed on the honeycomb core 12 in a state in which through holes 18 having a hole pattern: square holes, a diameter of 1 mm, a distance between hole centers of 5.5 mm and an aperture ratio of 23% It was arranged.
  • a woven fabric was used as the sound absorber 22 between the honeycomb core 12 and the perforated paper (first surface plate 16) made of kraft paper having the through holes 18.
  • Example 21 a color broad of 1 mm or less was used as the woven fabric. Bonding between the kraft paper (first face plate 16) and the sound absorbing material 22 (woven fabric) and between the kraft paper (first face plate 16) and the honeycomb core 12 were fixed. The same adhesive as used in Example 1 was used for adhesive fixing.
  • FIG. 24 shows the normal incidence sound absorption coefficient of Example 21 measured with an acoustic tube in the same manner as Example 1 described above. As shown in FIG. 24, even when the woven fabric of Example 21 is used as the sound absorber 22, it is understood that the sound absorption center frequency is high and the band is wide.
  • Examples 31 to 32 have the same configuration as Example 21 which is the soundproof structure 10C shown in FIGS. 22 and 23, and the sound absorber 22 is 25 ⁇ m in diameter made of aluminum foil with a thickness of 20 ⁇ m instead of woven fabric.
  • the difference is that the fine through-hole plate 24 is used in the form of a film-like fine through-hole plate 26 opened at an aperture ratio of 6.2%.
  • the through holes 18 are perforated by punching in kraft paper (perforated paper) which is the first surface plate 16
  • the holes do not become completely straight holes, and as shown in FIG. 25 or FIG.
  • the diameter of the hole on the side is different from the diameter of the hole on the opposite side (the fine through hole plate 26 side).
  • Example 31 as shown in FIG.
  • the hole shape of the through hole 18A (18) of kraft paper, which is the first surface plate 16 has a hole diameter on the honeycomb core 12 smaller than the hole diameter on the opposite side. It was a shape, that is, a downward convex shape.
  • the hole shape of the through hole 18B (18) of kraft paper which is the first surface plate 16 of the thirty-second embodiment is the honeycomb core 12 side as shown in FIG. The hole diameter was larger than the opposite hole diameter, i.e., convex upward.
  • FIG. 27 shows the normal incidence sound absorption coefficient of each of Examples 31 and 32 measured with an acoustic tube in the same manner as Example 1 described above.
  • Example 31 having a through hole 18A having a downward convex hole shape exhibits a higher sound absorption coefficient than Example 32 having a through hole 18B having a downward convex hole shape, It can be seen that the sound absorption characteristics are good.
  • the through hole 18 is punched in the first surface plate 16 by burring, burrs are generated at the edge of the hole having the smaller diameter.
  • the sound absorbing body 22 is attached to the surface of the first front plate 16 having the burrs, the burrs do not adhere well because the burrs are present.
  • a protrusion such as a burr around the hole on the edge of the hole on the opposite surface (the surface in contact with air) of the sound absorbing body 22
  • the sound absorption characteristics shown in FIG. 27 are worse when the sound absorber 22 is attached to the surface of the first surface plate 16 having the larger diameter of the through holes 18B than in the reverse case.
  • the manufacturing suitability is excellent. Therefore, when priority is given to manufacturing characteristics, the structure shown in FIG. 26 may be employed.
  • the cover layer 23 may be disposed on the outer side (upper side in FIG. 28) of the sound absorber 22.
  • the soundproof structure 11A shown in FIG. 28 includes a honeycomb core 12 having an opening 14, a plate-like first surface plate 16 having a through hole 18, and a second surface plate 20.
  • the cover layer 23 is further provided outside the sound absorber 22 (upper side in FIG. 12). Although only one opening 14 of the honeycomb core 12 and one through hole 18 of the first surface plate 16 are illustrated in FIG. 28, a plurality of the openings 14 and the through holes 18 of the first surface plate 16 are provided as shown in FIG. Also good.
  • the cover layer 23 is preferably a breathable layer for protection such as prevention of scattering of the sound absorber 22 and for design for enhancing the design, and is, for example, a mesh such as woven fabric, nonwoven fabric, polyester double mesh, etc. The thing can be used.
  • the cover layer 23 is a thing which does not change the sound absorption characteristic of the soundproof structure of this invention.
  • the total acoustic resistance of the cover layer 23, the first surface plate 16 and the sound absorber 22 is preferably 10 to 50000 Rayls, more preferably 50 to 10000 Rayls, and 100 to 2000 Rayls. Is more preferred.
  • the acoustic resistance of the cover layer 23 is preferably 1 to 10000 Rayls, more preferably 5 to 5000 Rayls, and still more preferably 10 to 1000 Rayls.
  • the total flow resistance of the ventilation flow resistance R1 of the through hole 18 of the first surface plate 16, the ventilation flow resistance R2 of the sound absorber 22 and the ventilation flow resistance R3 of the cover layer 23 is 12 Rayls or more and 16700 Rayls or less Is preferred. The reason is that such total air flow resistance can provide a sound absorption effect of 10% or more at the resonance frequency.
  • the total ventilation flow resistance described above is 75 Rayls or more, more preferably 2570 Rayls or less, and more preferably 170 Rayls or more, and most preferably 1150 Rayls or less.
  • a more preferable range of the above total vent flow resistance is a value at which a sound absorption effect of 50% or more is obtained at the resonance frequency, and a most preferable after range of the above total vent flow resistance is 80% or more at the resonance frequency It is a condition under which a sound absorption effect can be obtained.
  • the ventilation flow resistance R2 of the sound absorber 22 is larger than the ventilation flow resistance R3 of the cover layer 23.
  • the reason is that the cover layer 23 is likely to come in contact with an object, and the air flow resistance value is easily changed. Controlling the sound absorption is because the sound absorption effect is stabilized.
  • the unit flow resistance ⁇ is five types of 1000 Rayls / m, 5000 Rayls / m, 10000 Rayls / m, 25000 Rayls / m, and 50000 Rayls / m, and the thickness is 5 types of 5 mm, 10 mm, 20 mm, 50 mm, and 100 mm. there were.
  • the noise reduction rates (dB) of these 25 types of soundproof structures 11 were simulated as described above.
  • FIG. 29 shows the case where a unit flow resistance R is 1000 Rayls / m and a 10 mm thick sound absorber 22 is used.
  • FIG. 29 shows the case where a unit flow resistance R is 1000 Rayls / m and a 10 mm thick sound absorber 22 is used.
  • FIG. 30 shows a case where a unit flow resistance R is 5000 Rayls / m and a sound absorber 22 having a thickness of 10 mm is used.
  • FIG. 31 shows the case where a unit flow resistance R is 10000 Rayls / m and a sound absorber 22 having a thickness of 10 mm is used.
  • FIG. 32 shows the case where a unit flow resistance R is 25000 Rayls / m and a 10 mm thick sound absorber 22 is used.
  • the noise reduction amount itself is as low as 1 dB or less in the preferable configuration of the present invention (aperture ratio 5% or more, hole diameter 1 mm or more) It can be seen that the amount of noise reduction (dB) becomes smaller due to shoulder lowering.
  • the amount of muffling becomes large at 1.4 dB or more, the radius a is small, and the amount of muffling is large
  • the amount of noise reduction (dB) decreases with a falling shoulder, it can be seen that when the radius a is large, the amount of noise reduction (dB) increases with an increase in the right shoulder.
  • the unit flow resistance R of the sound absorber 22 shown in FIG. 31 is 10000 Rayls / m
  • the muffling amount is further increased to 1.9 dB or more, the radius a is the smallest, and the muffling amount is originally large.
  • the noise reduction amount (dB) is slightly reduced in the case where the right shoulder is lowered, but it can be seen that the noise cancellation amount (dB) is increased in the case of the right shoulder when the radius a is large.
  • the unit flow resistance R of the sound absorber 22 shown in FIG. 32 is 25000 Rayls / m or more
  • the amount of muffling is further increased to 2.5 dB or more in all cases in the configuration of the present invention, and muffling occurs at the upper right
  • the amount (dB) increases.
  • the flow resistance per unit length of the sound absorber is preferably 5000 Rayls / m or more, more preferably 10000 Rayls / m or more, and still more preferably 25000 Rayls / m or more.
  • the soundproof structure 10 may be formed at a position near the height of (a person's face).
  • the soundproof structure 10 of the present invention is formed in the central portion of the sound absorbing panel 42, and the Helmholtz resonance structure 44 or the like having a sound absorption peak on the lower frequency side of the soundproof structure 10 of the present invention in the peripheral portion. This is preferable because the sound absorption characteristics on the low frequency side of the panel sound absorption 42 can be improved and the sound absorption band can be expanded.
  • the sound absorbing panel 42 should be disposed instead of the sound absorbing panel 40 in the structure shown in FIG. Is preferred.
  • the soundproof structures 10A, 10B, 10C, 11, and 11A of the present invention may be used instead of the soundproof structure 10 of the present invention.
  • the sound absorber 22 is joined without any gap to the surface of the first surface plate 16 which is a perforated plate having the through holes 18.
  • the gap d between the first surface plate 16 and the sound absorber 22 (the cloth 52) is preferably more than 0 mm and 10 mm or less.
  • the gap d is more preferably 0.5 mm or more and 5 mm or less.
  • the entire surface of the sound absorber 22 may have no gap, and a portion is in contact with the first surface plate 16 which is a perforated plate. You may
  • the sound absorber 22 (cloth 52) made of cloth (color broad) is attached to the first face plate 16 without a gap
  • the sound absorber 22 (cloth 52) made of cloth (color broad)
  • the gap d between the first front plate 16 and the sound absorbing body 22 is 1 mm to 3 mm
  • the frequency is 500 Hz to 1500 Hz as compared with the solid line without any gap. It can be seen that the sound absorption characteristics are improved on the low frequency side.
  • the first surface plate 16 and the sound absorber 22 are used as a structure for opening such a gap between the first surface plate 16 and the sound absorber 22 (the cloth 52).
  • the first surface plate 16, the honeycomb core 12, and the second surface plate 20 are used.
  • It may be a frame 56 for giving strength to the end of the integrated panel 54 made of
  • the opposing side surfaces of the panel 54 are fixed by a reinforcing frame 56 made of paper or the like to be integrated, and the panel 53 and the frame are covered so as to cover the frame 54.
  • the whole of the body 56 may be wrapped by the sound absorbing body 22 (cloth 52).
  • a surface fastener magnetic tape (registered trademark)
  • a magnet or the like may be used to allow the sound absorber 22 (the cloth 52) to be removable from the panel 54.
  • hook surfaces 58a constituting the surface fasteners 58 are attached and fixed to opposite ends of the first surface plate 16 of the panel 54, respectively.
  • the loop surface 58b which comprises the surface fastener 58 may be attached and fixed to the opposing both ends of 52), respectively, and the sound absorbing body 22 (cloth 52) may make the 1st surface board 16 of the panel 54 detachable.
  • the hook surface 58a and the loop surface 58b of the surface fastener 58 are provided at both ends of the first surface plate 16 and at both ends of the sound absorber 22 (the cloth 52), respectively. It may be provided on both ends of the cloth 22 (cloth 52) and on both ends of the first surface plate 16, or may be changed every end. Furthermore, instead of the hook surface 58a and the loop surface 58b of the surface fastener 58, a removable climate or structure such as a magnet and a stainless steel sheet may be used, for example.
  • the soundproof structure according to the present invention is, for example, inside or outside of a building or other structure (for example, a wall, ceiling panel, etc. for housing, hall, elevator, music classroom, meeting room, etc.), animal (especially , Pet), and transportation applications such as interiors of automobiles, and logistics applications such as box materials and packing materials.
  • a building or other structure for example, a wall, ceiling panel, etc. for housing, hall, elevator, music classroom, meeting room, etc.), animal (especially , Pet), and transportation applications such as interiors of automobiles, and logistics applications such as box materials and packing materials.

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  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Engineering & Computer Science (AREA)
  • Multimedia (AREA)
  • Architecture (AREA)
  • Electromagnetism (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Laminated Bodies (AREA)

Abstract

L'invention concerne une structure d'insonorisation comprenant : un noyau en nid d'abeilles; une première plaque superficielle et une seconde plaque superficielle qui prennent en sandwich le noyau en nid d'abeilles; des trous traversants perforés dans la première plaque superficielle; et un corps absorbant le son disposé sur une surface extérieure de la première plaque superficielle, ladite surface extérieure se trouvant sur le côté opposé à celui du noyau en nid d'abeilles. Le diamètre des trous traversants dans la première plaque superficielle est d'au moins 1,0 mm et le rapport d'ouverture des trous traversants est d'au moins 1,0 %, et lorsque l est l'épaisseur du nid d'abeilles, que h est l'épaisseur de la première plaque superficielle, et que Ar est le rapport d'ouverture, les conditions de l'inégalité (1) ci-dessous sont satisfaites. Cette structure d'insonorisation permet d'obtenir une enceinte d'insonorisation et une cellule d'insonorisation robustes et légères, permettant une absorption de son à large bande et présentant des performances d'absorption de son améliorées. f1(1,h)×1n(ar)+f2(1,h)≥1,5 …(1) Ici, f1(1,h)=A1(h)×12+A2(h)×1+0,24915, f2(1,h)=A3(h)×12+A4(h)×1+1,2804, A1(h)=19,466×1n(h)-0,3038 A2(h)=-1,611×1n(h)+4,0162 A3(h)=119,22×1n(h)+78,249 A4(h)=-5 689,7×h+94,861
PCT/JP2018/048363 2018-01-10 2018-12-27 Structure d'insonorisation, enceinte d'insonorisation et cellule d'insonorisation Ceased WO2019138920A1 (fr)

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JP2018001876 2018-01-10
JP2018-001876 2018-01-10
JP2018120999 2018-06-26
JP2018-120999 2018-06-26
JP2018-206720 2018-11-01
JP2018206720 2018-11-01

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WO2021085957A1 (fr) * 2019-10-31 2021-05-06 전북대학교산학협력단 Couvercle d'isolation phonique pour corps rotatif
CN114730559A (zh) * 2019-10-31 2022-07-08 赛峰短舱公司 声音衰减板及其制造方法

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KR102168237B1 (ko) * 2020-08-20 2020-10-20 주식회사 수정유리 Pvb필름 또는 수지접합 tps 또는 알루미늄 금속 복층 유리 구조체
JP2022039256A (ja) * 2020-08-28 2022-03-10 株式会社熊谷組 吸遮音壁

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JP2010191029A (ja) * 2009-02-17 2010-09-02 Yamaha Corp 吸音構造体、吸音構造体群および音響室
JP2012013912A (ja) * 2010-06-30 2012-01-19 Three M Innovative Properties Co 吸音システム及びその作製方法
JP2012103556A (ja) * 2010-11-11 2012-05-31 Kitagawa Ind Co Ltd 吸音体
JP2017151256A (ja) * 2016-02-24 2017-08-31 宇部エクシモ株式会社 中空構造板及び吸音構造体
WO2017170353A1 (fr) * 2016-03-29 2017-10-05 富士フイルム株式会社 Structure d'insonorisation, structure de séparation, élément de fenêtre et cage

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JPS6314300U (fr) * 1986-07-12 1988-01-29
US6182787B1 (en) * 1999-01-12 2001-02-06 General Electric Company Rigid sandwich panel acoustic treatment
JP2010191029A (ja) * 2009-02-17 2010-09-02 Yamaha Corp 吸音構造体、吸音構造体群および音響室
JP2012013912A (ja) * 2010-06-30 2012-01-19 Three M Innovative Properties Co 吸音システム及びその作製方法
JP2012103556A (ja) * 2010-11-11 2012-05-31 Kitagawa Ind Co Ltd 吸音体
JP2017151256A (ja) * 2016-02-24 2017-08-31 宇部エクシモ株式会社 中空構造板及び吸音構造体
WO2017170353A1 (fr) * 2016-03-29 2017-10-05 富士フイルム株式会社 Structure d'insonorisation, structure de séparation, élément de fenêtre et cage

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WO2021085957A1 (fr) * 2019-10-31 2021-05-06 전북대학교산학협력단 Couvercle d'isolation phonique pour corps rotatif
CN114730559A (zh) * 2019-10-31 2022-07-08 赛峰短舱公司 声音衰减板及其制造方法

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