EP2157567A2 - Schalldämmende Struktur unter Verwendung eines porösen Mediums mit geschlossenen Poren - Google Patents

Schalldämmende Struktur unter Verwendung eines porösen Mediums mit geschlossenen Poren Download PDF

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Publication number
EP2157567A2
EP2157567A2 EP09010237A EP09010237A EP2157567A2 EP 2157567 A2 EP2157567 A2 EP 2157567A2 EP 09010237 A EP09010237 A EP 09010237A EP 09010237 A EP09010237 A EP 09010237A EP 2157567 A2 EP2157567 A2 EP 2157567A2
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EP
European Patent Office
Prior art keywords
closed
porous material
sound absorbing
vibration member
cell porous
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EP09010237A
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English (en)
French (fr)
Inventor
Rento Tanase
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Yamaha Corp
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Yamaha Corp
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    • 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 sound absorbing structures using closed-cell porous media.
  • the present invention also relates to sound chambers using sound absorbing structures.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2003-316364
  • Patent Document 2 Japanese Unexamined Patent Application Publication No.
  • Patent Document 1 discloses sound absorbing media using open-cell porous materials (or cellular porous materials), which are well known in the fields of sound absorbing technology.
  • Patent Document 2 discloses sound absorbing media using open-cell porous materials and closed-cell porous materials with an airflow rate of 0.1 dm 3 /s or more. A high airflow rate does not cause a sound pressure difference between the surface and the backside of the porous material, which in turn makes it difficult for a plate vibration member to vibrate, thus degrading a sound absorbing effect of a plate-vibration sound absorbing structure.
  • the present invention aims at demonstrating a high sound absorbing effect in a low frequency range with a thin sound absorbing structure whose total thickness (i.e. the sum of the thickness of a porous material and the thickness of a rear air cavity) is about 50 mm.
  • a sound absorbing structure of the present invention is constituted of a vibration member composed of a closed-cell porous material, and an air cavity formed in the rear side of the vibration member.
  • the vibration member is formed by laminating an open-cell porous material with the closed-cell porous material or by laminating an air-permeable member with the closed-cell porous material.
  • an airflow rate of the closed-cell porous material be less than 0.1 dm 3 /s.
  • a sound absorbent group is formed using a plurality of sound absorbing structures, each of which is constituted of the vibration member and the air cavity.
  • a sound chamber is formed using at least one sound absorbing structure including the vibration member and the air cavity.
  • the sound absorbing structure of the present invention is a plate/film-vibration sound absorbing structure in which the air cavity formed inside the housing is closed with the vibration member composed of the closed-cell porous material, wherein it is possible to prevent the degradation of the vibration member while securing high sound absorption characteristics, thus improving the reliability in sound absorption.
  • Fig. 1 is a perspective view showing the constitution of a sound absorbing structure according to a preferred embodiment of the present invention.
  • Fig. 2 is an exploded perspective view of the sound absorbing structure which is constituted of a housing, a vibration member, and an air cavity.
  • Fig. 3A is a sectional view taken along line III-III in Fig. 1 showing that the housing is covered with the vibration member composed of a closed-cell porous material.
  • Fig. 3B is a sectional view taken along line III-III in Fig. 1 showing that the housing is covered with the vibration member composed of a closed-cell porous material and an open-cell porous material.
  • Fig. 3C is a sectional view taken along line III-III in Fig. 1 showing that the housing is covered with the vibration member composed of a closed-cell porous material and an air-permeable member.
  • Fig. 4A is a sectional view diagrammatically showing the closed-cell porous material including a plurality of closed cells.
  • Fig. 4B is a sectional view diagrammatically showing the open-cell porous material including a plurality of open cells.
  • Fig. 5 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 10-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 6 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 20-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 7 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 30-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 8 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 10-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 9 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 20-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 10 is a graph showing open-cell and closed-cell characteristic curves based on experimental results with a 30-mm-thickness air cavity formed in the rear side of the vibration member in the sound absorbing structure.
  • Fig. 11 is a graph showing simulation results of normal incidence sound absorption coefficients on a sound absorbing structure according to a third variation of the present embodiment, wherein five characteristic curves are plotted with respect to various surface densities at the center of the vibration member.
  • Fig. 1 is a perspective view showing the constitution of a sound absorbing structure 10 according to a preferred embodiment of the present invention.
  • Fig. 2 is an exploded perspective view of the sound absorbing structure 10.
  • Figs. 3A to 3C are sectional views taken along line III-III in Fig. 1 .
  • Figs. 1 and 2 and Figs 3A to 3C are illustrated with prescribed dimensions, which do not precisely match the actual design dimensions, in order to distinctively show the constituent elements of the sound absorbing structure 10.
  • the sound absorbing structure 10 is constituted of a housing 20 (serving as the base of the sound absorbing structure 10), a vibration member 30 for covering an opening 23 of the housing 20, and an air cavity 40 which is formed inside the housing 20 equipped with the vibration member 30.
  • the housing 20 is formed in a closed-bottom rectangular prismatic shape composed of a synthetic resin (e.g. an ABS resin), which is constituted of a base 21 and a side wall 22 as well as the opening 23.
  • the base 21 is disposed opposite to the opening 23, while the side wall 22 is disposed to encompass the opening 23.
  • the vibration member 30 is a squared board composed of a high polymer compound (e.g. a silicon foam, a urethane foam, a polyethylene foam, an ethylene-propylene rubber foam, etc.).
  • the periphery of the vibration member 30 is bonded to the edge of the opening 23. Since the vibration member 30 is fixed upon the opening 23 of the housing 20, a tightly-closed air cavity 40 is formed inside the sound absorbing structure 10 (or in the rear side of the vibration member 30).
  • the vibration member 30 is not necessarily formed in a plate (or board) shape but is formed in a film (or membrane) shape. In short, the present embodiment requires that the vibration member 30 be formed of any type of material which is deformable upon receiving an external force and is restorable in shape due to elasticity.
  • the plate shape is defined as a thin three-dimensional shape (or a rectangular parallelepiped shape) which is reduced in thickness and is enlarged in a two-dimensional area, while the film shape (or sheet shape) is further reduced in thickness compared to the plate shape and is restorable in shape due to tension.
  • the vibration member 30 is formed in a prescribed shape and of a prescribed material which is reduced in terms of a rigidity (i.e. a Young's modulus, a thickness, and a geometrical moment of inertia) and/or a mechanical impedance, i.e. 8x ⁇ (bending rigidity)x(surface density) ⁇ 1/2 , in comparison with the housing 20. That is, the vibration member 30 possesses elastic-vibration ability relative to the housing 20, so that the sound absorbing structure 10 demonstrates the sound absorbing operation by means of the vibration member 30.
  • a rigidity i.e. a Young's modulus, a thickness, and a geometrical moment of inertia
  • a mechanical impedance i.e. 8x ⁇ (bending rigidity)x(surface density) ⁇ 1/2
  • the sound absorbing structure 10 having the above basic constitution is characterized in that the vibration member 30 is formed using a closed-cell porous material 50 shown in Fig. 3A .
  • the airflow rate of the closed-cell porous material 50 is less than 0.1 dm 3 /s, thus shutting off an airflow therethrough.
  • the closed-cell porous material it is possible to use a silicon foam and an ethylene-propylene rubber foam (or EPDM, i.e. ethylene-propylene-diene-methylene rubber), for example.
  • Figs. 4A and 4B illustrate the cross-sectional comparison between the closed-cell porous material 50 and an open-cell porous material 60.
  • closed-cell porous material 50 shown in Fig. 4A a plurality of closed cells 51 do not communicate with each other and overlap with each other so that they are independent of each other.
  • the closed-cell porous material 51 having elasticity serves as an integrally vibrating board, in other words, the closed-cell porous material 51 has elasticity but does not have air permeability.
  • Fig. 4A diagrammatically shows that the closed cells 51 are regularly aligned, but they may be aligned in a random manner; that is, the closed-cell porous material 50 includes the closed cells 51, which do not overlap with each other, so as to prevent an airflow occurring between the surface and the backside thereof.
  • a plurality of open cells 61 partially overlap with each other and communicate with each other; hence, the open-cell porous material 60 has a sponge-like texture dependent upon the material and the size of the cell 61.
  • Fig. 4B diagrammatically shows that the open cells 61 are regularly aligned, but they may be aligned in a random manner; that is, the open-cell porous material 60 includes the open cells 61, which adjoin together to partially overlap with each other, so as to establish an air flow occurring between the surface and the backside thereof.
  • the sound absorbing structure 10 serves as a spring-mass system composed of the mass of the vibration member 30 and the spring component of the air cavity 40.
  • a resonance frequency f [Hz] of the spring-mass system is given by equation (1) using an air density ⁇ 0 [kg/m 3 ], the speed of sound c 0 [m/s], a density ⁇ [kg/m 3 ], a thickness t [m] of the vibration member 30, and a thickness L [m] of the air cavity 40.
  • f 1 2 ⁇ ⁇ ⁇ ⁇ 0 ⁇ c 0 2 ⁇ tL 1 / 2
  • the sound absorbing structure 10 includes the vibration member 30 having elasticity subjected to elastic vibration, a bending system (representing the elastic vibration) is applied to the spring-mass system.
  • a resonance frequency f [Hz] of a plate/film-vibrating sound absorbing structure is given by equation (2) using a one-side length "a" [m] and another-side length "b” [m] of the rectangular shape of the vibration member 30, a Poisson ratio ⁇ [-] of the vibration member 30, and integral numbers p, q.
  • the calculation result of the above resonance frequency f is used for architectural acoustic designs.
  • the resonance frequency f represents the sum of the term of the spring-mass system " ⁇ 0 c 0 2 / ⁇ tL" and the term of the bending system (i.e. the term directly subsequent to the term of the spring-mass system).
  • the spring-mass system of the vibration member 30 and the bending system representing the elastic vibration form important factors determining the sound absorbing condition for the sound absorbing structure 10.
  • the vibration member 30 is subjected to elastic vibration dependent upon the difference between the external sound pressure applied to the exterior surface of the vibration member 30 and the internal sound pressure occurring inside the air cavity 40, in other words, the sound-pressure difference between the surface and the backside of the vibration member 30. Sound is absorbed in such a way that energy of sound waves reaching the sound absorbing structure 10 is consumed by way of the vibration of the vibration member 30.
  • the vibration member 30 absorbs sound in a certain frequency range whose center frequency corresponds to the resonance frequency f according to equation (2).
  • Figs. 5 to 7 are graphs of characteristic curves representing results of experiments in which sounds having various frequencies are applied to sound absorbing structures (i.e. experimental subjects) so as to measure normal incidence sound absorbing coefficients.
  • Figs. 5 to 7 show experimental results with respect to two types of sound absorbing structures, one of which includes an open-cell type vibration member composed of a 10-mm-thickness open-cell urethane foam and the other of which includes a closed-cell type vibration member composed of a 10-mm-thickness closed-cell silicon foam. That is, an open-cell characteristic curve A represents the sound absorption characteristic regarding the open-cell type vibration member, while a closed-cell characteristic curve B represents the sound absorption characteristic regarding the closed-cell type vibration member.
  • Figs. 5 to 7 differ from each other in terms of the thickness of an air cavity formed in the rear side of the vibration member; that is, Fig. 5 shows the experimental result with regard to a 10-mm-thickness air cavity; Fig. 6 shows the experimental result with regard to a 20-mm-thickness air cavity; and Fig. 7 shows the experimental result with regard to a 30-mm-thickness air cavity.
  • the open-cell characteristic curves A of Figs. 5 to 7 show that sound absorption coefficients decrease in a low frequency range but increase in a high frequency range, while the closed-cell characteristic curves B show that sound absorption coefficients peak at maximum values in a further low frequency range.
  • the sound absorbing structure 10 including the vibration member 30 composed of a closed-cell porous material demonstrates an adequate sound absorbing effect.
  • the density of the closed-cell porous material is set to 250 kg/m 3
  • the density of the open-cell porous material is set to 35 kg/m 3 .
  • Figs. 8 to 10 show experimental results with respect to two types of sound absorbing structures, one of which includes an open-cell type vibration member composed of a 10-mm-thickness open-cell urethane foam and the other of which includes a closed-cell type vibration member composed of a 10-mm-thickness closed-cell EPDM, i.e. an ethylene-propylene-diene-methylene rubber.
  • an open-cell characteristic curve A represents the sound absorption characteristic regarding the open-cell type vibration member
  • a closed-cell characteristic curve B represents the sound absorption characteristic regarding the closed-cell type vibration member.
  • Figs. 8 to 10 differ from each other in terms of the thickness of an air cavity formed in the rear side of the vibration member; that is, Fig. 8 shows the experimental result with regard to a 10-mm-thickness air cavity; Fig. 9 shows the experimental result with regard to a 20-mm-thickness air cavity; and Fig. 10 shows the experimental result with regard to a 30-mm-thickness air cavity.
  • the sound absorbing structure 10 including the vibration member 30 composed of the closed-cell porous material 50 is capable of absorbing sound in a low frequency range regardless of the "slim" thickness of the vibration member 30 and the air cavity 40 in total which is 50 mm or less.
  • the closed-cell porous material 50 shuts off an airflow therethrough, it is possible to prevent external air from entering into the air cavity 40 via the vibration member 30 even when the sound absorbing structure 10 is positioned in a dusty sound field or environment. That is, it is possible to prevent the air cavity 40 from being contaminated with dust or foreign matter.
  • the closed-cell porous material 50 inherently blocks air or humidity entering therein, it is possible to enhance the durability of the vibration member 30 and to thereby improve the reliability of the sound absorbing structure 10.
  • the closed-cell porous material 50 is lower in manufacturing cost than the open-cell porous material 60, it is possible to manufacture the sound absorbing structure 10 at a relatively low cost. Since it is easier to perform cutting on the closed-cell porous material 50 rather than the open-cell porous material 60, it is possible to improve the productivity. As described above, the present embodiment demonstrates various outstanding effects.
  • the present embodiment exemplifies the sound absorbing structure 10 including the vibration member 30 composed of the closed-cell porous material 50, which can be modified in various ways.
  • Fig. 3B is a sectional view of a vibration member 31 in which the open-cell porous material 60 is laminated on the surface (i.e. the sound-incidence side) of the closed-cell porous material 50.
  • the vibration member 31 is fixed to the housing 20 in such a way that the air cavity 40 is formed in the rear side of the closed-cell porous material 50.
  • Fig. 3C is a sectional view of a vibration member 32 in which an air-permeable member 70 composed of a fabric material such as a mesh, cloth, and flocked fabric is laminated on the surface (i.e. the sound-incidence side) of the closed-cell porous material 50.
  • the vibration member 32 is fixed to the housing 20 in such a way that the air cavity 40 is formed in the rear side of the closed-cell porous material 50.
  • the vibration member 31 it is possible to further modify the vibration member 31 such that three or more layers of the open-cell porous material 60 are laminated on the closed-cell porous material 50.
  • the first variation requires that the vibration member be formed using the closed-cell porous material 50 so as to reliably shut off the airflow occurring between the air cavity 40 and the external air.
  • the present inventor performed various detailed experiments so as to determine inequality (3) regarding the relationship between a fundamental frequency fa of the bending system and a resonance frequency fb of the spring-mass system.
  • inequality (3) the present inventor actually verified an improvement of the sound absorption, since the fundamental vibration of the bending system cooperates with the spring component of the rear air cavity so that a relatively high amplitude of vibration occurs in a frequency band between the resonance frequency of the spring-mass system and the fundamental frequency of the bending system, i.e. (resonance frequency fa of bending system) ⁇ (peak sound-absorption frequency f) ⁇ (fundamental frequency fb of spring-mass system).
  • the sound absorbing structure including parameters according to inequality (4) is suitable for absorbing sound in a low frequency range which is 300 Hz or less, since the fundamental frequency of the bending system is sufficiently lowered due to a low-degree elastic vibration mode.
  • the present embodiment exemplifies the sound absorbing structure 10 which is constituted of the rectangular housing 20, the vibration member 30 for closing the opening 23 of the housing 20, and the air cavity 40 formed inside the housing 20.
  • the housing 20 is not necessarily formed in a rectangular shape, which can be changed to other shapes such as a circular shape and a polygonal shape.
  • the sound absorbing structure 10 possesses a sound absorption mechanism composed of the spring-mass system and the bending system.
  • the present inventor performed experiments on sound absorption coefficients at resonance frequencies with various surface densities applied to the vibration member 30.
  • Fig. 11 show simulation results on normal incidence sound absorption coefficients with respect to the sound absorbing structure 10, in which the vibration member 30 having the length and breadth of 100 mm ⁇ 100 mm and the thickness of 0.85 mm is fixed to the housing 20 containing the air cavity 40 having the length and breadth of 100 mm ⁇ 100 mm and the thickness of 10 mm and in which the surface density is changed with respect to the center portion having the length and breadth of 20 mm ⁇ 20 mm and the thickness of 0.85 mm.
  • the simulation is performed based on JIS A 1405-2 (titled “Acoustics - Determination of sound absorption coefficient and impedance in impedance tubes - Part 2: Transfer-function method") so as to determine a sound field of a sound chamber for arranging the sound absorbing structure 10 in accordance with the finite element method, thus calculating sound absorption characteristics by way of transfer functions.
  • Fig. 11 shows five characteristic curves D1 to D5 which are plotted using the same surface density of the periphery of the vibration member 30 of 799 g/m 2 while changing the surface density of the center portion of the vibration member 30 as 399.5 g/m 2 799 g/m 2 , 1199 g/m 2 , 1598 g/m 2 , and 2297 g/m 2 in D1, D2, D3, D4, and D5 respectively.
  • the average density of the vibration member 30 is set to 783 g/m 2 , 799 g/m 2 , 815 g/m 2 831 g/m 2 , and 863- g/m 2 in D1, D2, D3, D4, and D5 respectively.
  • the simulation results of Fig. 11 clarify that sound absorption coefficients peak in a frequency range between 300 Hz and 500 Hz and at a frequency around 700 Hz.
  • Sound absorption coefficients peak around 700 Hz due to the resonance of the spring-mass system composed of the mass of the vibration member 30 and the spring component of the air cavity 40.
  • the sound absorbing structure 10 absorbs sound in such a way that the sound absorption coefficient peaks at the resonance frequency of the bending system in a low frequency range, wherein the resonance frequency of the bending system gradually decreases as the surface density of the center portion of the vibration member 30 increases.
  • the resonance frequency of the bending system is determined by the equation of motion directing the elastic vibration of the vibration member 30 and varies in inverse proportion to the surface density of the vibration member 30.
  • the resonance frequency is greatly affected by the density of the antinode of the characteristic vibration (at which the amplitude becomes maximum).
  • the simulation is performed by changing the surface density of the center portion with respect to the antinode region of 1 ⁇ 1 characteristic mode, thus causing variations of the resonance frequency of the bending system.
  • the simulation result clarifies that, by increasing the surface density of the center portion to be higher than the surface density of the periphery, the prescribed frequencies causing peak sound absorption coefficients are further lowered in a low frequency range.
  • the prescribed frequencies causing peak sound absorption coefficients are further lowered in a low frequency range.
  • the sound absorbing structure 10 is capable of shifting the prescribed frequency causing a peak sound absorption coefficient by simply changing the surface density of the center portion of the vibration member 30, it is possible to lower the sound absorption frequency without greatly changing the overall weight of the sound absorbing structure 10 in contrast to a typical example of the sound absorbing structure whose sound absorption frequency is changed by increasing the overall weight.
  • a sound absorbent group including a plurality of sound absorbing structures it is possible to form a sound absorbent group including a plurality of sound absorbing structures according to one of the present embodiment and variations. Alternatively, it is possible to form a sound absorbent group including a plurality of sound absorbing structures having different sound absorption characteristics or a plurality of sound absorbing structures having three or more different sound absorption characteristics.
  • the sound absorbing structure and the sound absorbent group are applicable to various types of sound chambers having controlled acoustic characteristics such as soundproof chambers, halls, theaters, listening rooms of audio devices, conference rooms, compartment spaces of transportation such as vehicles, and housings of speakers and musical instruments.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Building Environments (AREA)
EP09010237A 2008-08-20 2009-08-07 Schalldämmende Struktur unter Verwendung eines porösen Mediums mit geschlossenen Poren Withdrawn EP2157567A2 (de)

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JP2008211972A JP5245641B2 (ja) 2008-08-20 2008-08-20 吸音構造体

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