US3783968A - Sound barrier - Google Patents

Sound barrier Download PDF

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US3783968A
US3783968A US00319379A US3783968DA US3783968A US 3783968 A US3783968 A US 3783968A US 00319379 A US00319379 A US 00319379A US 3783968D A US3783968D A US 3783968DA US 3783968 A US3783968 A US 3783968A
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sound barrier
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C Derry
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01F—ADDITIONAL WORK, SUCH AS EQUIPPING ROADS OR THE CONSTRUCTION OF PLATFORMS, HELICOPTER LANDING STAGES, SIGNS, SNOW FENCES, OR THE LIKE
    • E01F8/00—Arrangements for absorbing or reflecting air-transmitted noise from road or railway traffic
    • E01F8/0005—Arrangements for absorbing or reflecting air-transmitted noise from road or railway traffic used in a wall type arrangement
    • E01F8/0047—Arrangements for absorbing or reflecting air-transmitted noise from road or railway traffic used in a wall type arrangement with open cavities, e.g. for covering sunken roads
    • E01F8/0052—Grate-style, e.g. as wall facing

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  • ABSTRACT A sound barrier comprising a plurality of hollow, wedge-shaped, energy dissipating cells mounted in parallel, side-by-side, spaced relationship as inverseacting acoustic horns, first sides of all cells being coplanar.
  • Each of the cells has a plurality of openings in the remaining two sides thereof along the edges which are adjacent the first side and a plurality of elongated v openings along the apex defined by the intersection of the two sides.
  • Each cell is made in two interlocking parts, one part forming the first side and the other part forming the remaining two sides.
  • Each part comprises a thin outer shell of structurally rigid material and an inner lining of sound deadening material, such as polyurethane closed cell foam.
  • the present invention relates to sound barriers and, more particularly, to an inexpensive, effectively optically transparent, sound barrier which is capable of reflecting, absorbing, and converting sound energy to substantially lower levels ,under all atmospheric conditions.
  • a conventional barrier is in the form of a solid wall which can be in the form of earth or an upright barrier, the latter often made from concrete.
  • an effective earth barrier may be provided by constructing depressed roadways.
  • tests have shown that with simple barries, significant noise level reductions are achievable only at extreme Wall heights, in excess of 25 feet, and at higher frequencies, in excess of 1 kHz. With lower barrier heights, a maximum attenuation of dB is attainable, due to the influence of defraction effects over a barrier.
  • the proposed kinematic sound screen consists of a plurality of Helmholtz resonating chambers which are mounted in parallel, side-by-side, spaced relationship.
  • each chamber By providing each chamber with a triangular cross-section and positioning the chambers with first sides coplanar and the remaining two sides extending in the same direction, towards a source of sound, the walls of the chambers act as inverse-acting acoustic horns which focus the sound energy toward the openings of the Helmholtz resonating chambers, thus greatly increasing their efficiency.
  • Each chamber has a plurality of openings in each side thereof, at the focal point of the acoustic horns, which act as filters for the incident sound waves. It is stated that on the basis of laboratory experiments, the net effect of the attenuation phenomenon will exceed 25 dB, effectively 10 dB down from the defracted component of noise reported for conventional solid barriers.
  • the proposed kinematic sound screen consists of a series of wedges separated by thin apertures. An observer sees only a narrow angle of view through each aperture, but as the observer moves along a line of travel, the angle of view changes. Thus, an observer traveling at freeway speeds receives overlapping views of the field beyond the barrier within the time which the retina of the eye stores an image. By means of a serial strobe effect, the observer sees a series of views of the field which he interprets in much the same way as we view a TV or movie picture.
  • the use of the exterior walls of the wedge-shaped resonating chambers as multiple inverse-acting acoustic horns significantly effects the overall performance of the sound screen.
  • the acoustic horn is essentially a transformer, acting more efficiently than the oscillating mass alone because the horn creates a better impedance match between the resonating chamber and the external air. This means that high pressures are created in the throat area, causing the vibrating air mass at the neck of the Helmholtz chamber to achieve maximum resonant amplitudes in frequency bands near the resonant frequency of the chamber.
  • the net result of this air coupling effect is to maximize viscous energy losses for sound waves entering the Helmholtz chamber.
  • Helmholtz resonating chamber An integral part of the proposed kinematic sound screen is the Helmholtz resonating chamber.
  • a rigid enclosure of volume V connected to the external air mass through a small opening of effective length L and crosssectional area A has a resonance frequency to which can be expressed by the formula:
  • the theoretical operation of the Helmholtz resonating chamber is that the air in the cavity opening moves in and out as a unit under fluctuating pressure from the external air.
  • the pressure of the air inside the cavity changes as it is alternately compressed and expanded due to movement of the air in the cavity opening.
  • patterns of standing waves are generated within the chambers in addition to the oscillating mass of air at the cavity opening. These standing waves generate additional resonance frequencies which are higher than the fundamental frequency w, and have a significant effect on the frequency range over which damping occurs.
  • thephenomenon of oscillating air masses and standing waves within the chamber and at the chamber openings is substantially effected by wind currents and other atmospheric conditions.
  • wind currents and other atmospheric conditions For example, not only do the exterior walls of the chambers focus the incoming sound energy on the chamber openings, but they also focus wind currents thereon-These wind currents apparently modify substantially the pressure of the air inside the resonator cavities, thereby substantially modifying and'often eliminating or at least effectively reducing the energy cancellation properties of the chambers.
  • Changes in temperature and humidity also result in changing operating characteristics of the resonator chambers. Therefore, while such a sound barrier appears highly desirable and practical in theory, it is not as effective in practice.
  • a sound barrier which offers the potential for eliminating not only the above described disadvantages of conventional highway noise barriers but also for solving the problems inherent in sound barriers using Helmholtz resonating chambers and inverse-acting acoustic horns.
  • the present sound barrier is not only relatively inexpensive but is capable of reflecting, absorbing, and converting sound energy to substantially lower levels under all atmospheric conditions. With the present sound barrier, effective sound reduction is only slightly dependent upon barrier height and barrier heights of only 6 feet are capable of achieving attenuations of dB and more.
  • the present sound barrier blends aesthetically with the surrounding landscape and the motorist is not given the impression that he is captured within a tunnel since at'freeway speeds, the present sound barrier is visually transparent.
  • the present sound barrier is not effected by wind currents and other atmospheric conditions and operates as well in the field as in a testing chamber.
  • the present sound barrier comprises a plurality of hollow, energy dissipating cells, each having a triangular cross-section, mounted in parallel, side-byside, spaced relationship as inverse-acting acoustic horns, first sides of all cells being coplanar or aligned with a continuous, arcuate surface. Because of the spacing between adjacent cells, the barrier appears optically transparent at freeway speeds.
  • Each of the cells has a plurality of openings in the two remaining sides thereof along the edges which are adjacent the first side, which openings act as side branch filters for the incident sound waves and permit entrance of the pressure waves into the energy dissipating cells.
  • each cell has a plurality of elongated openings along the apex defined by the intersection of the two sides, which openings direct the incoming sound waves back upon themselves and prevent pressure buildups within the cells in the presence of air currents.
  • each cell acts as a sound energy exchanger, receiving air and sound waves, decreasing the level of the latter, and re-directing both in a definite, prescribed direction.
  • Each cell is made in two interlocking parts, one part preferably forming the first side and the other part forming the remaining two sides.
  • Each part comprises a thin outer shell of structurally rigid material, such as aluminum, steel, or plastic, and an inner lining of sound deadening material, such as polyurethane closed cellv foam or other sound absorbing material.
  • the cells may be mounted horizontally or vertically along a highway, freeway, or other heavily traveled thorough-fare or along the side of any other noise producing source.
  • FIG. I is a perspective view of a portion of a traffic thoroughfare with the present barrier in position along the side thereof;
  • FIG. 2 is an enlarged perspective view of aportion of the barrier of FIG. 1;
  • FIG. 3 is an enlarged cross sectional view taken along the line 33 in FIG. 2;
  • FIG. 4 is an enlarged cross-sectional view of a portion of the structure of FIG. 3 showing the interlocking connection between the two subassemblies of the present sound barrier;
  • FIG. 5 is an exploded view showing the construction of the thin outer shells of structurally rigid material of which the sound barrier of FIGS. l-4 is partially constructed;
  • FIG. 6 is a perspective view showing the manner in which the present sound barrier may be used along the side of an aircraft runway.
  • DESCRIPTICN OF THE PREFERRED EMBODIMENTS Soundpropagates through air as a series of fluctuations in the local air density,-pressure, and temperature, as well as disturbances in the positions of air particles. Since each set of fluctuations is repeated at regular intervals, this form of disturbance can be characterized as wave motion and treated as such for purposes of description.
  • FIG. 1 thereis shown a sound barrier, generally designated 10, positioned adjacent the side of a highway, freeway, or other heavily traveled roadway 11 on which cars 12, buses, trucks and the like travel.
  • sound barrier 10 consists of an assembly of hollow, energy dissipating cells, generally designated 20, each having a triangular cross-section, which are mounted in parallel, side-byside, relationship with a narrow breathing slot 15 therebetween.
  • Each cell 20 is identical and includes a first side 21, all of sides 211 typically being coplanar, as
  • Each cell 21 has two remaining sides 22 and 23 which all extend in the same direction, so that all of sides 22 are parallel and all of sides 23 are parallel.
  • Each cell 20 has a plurality of inlet openings 24 in each of sides 22 and 23, openings 24 being spaced along the edges of sides 22 and 23 which are adjacent sides 21.
  • Each of cells 20 further has a plurality of outlet openings 25 along the leading edge or apex thereof defined by the intersection of sides 22 and 23. As will be described more fully hereinafter, the size, area, and number of openings 24 and 25 are chosen to determine the correct efficiency of sound barrier 10.
  • each of cells 20 consist of two Subassemblies, a rectangular subassembly 26 from which side 21 is constructed and a triangular subassernbly 27 from which sides 22 and 23 are constructed.
  • Subassemblies 26 and 27 preferably comprise thin outer shells 28 and 29, respectively, of structurally rigid material, such as fiberglass, plastic, wood, concrete, or a sheet or extruded metal such as aluminum.
  • Subassemblies 26 and 27 are also preferably lined with sound deadening materials 30 and 31, respectively. Many suitable sound deadening materials are known but a preferred material is polyurethane closed cell foam, foamed in place, and containing a bonding agent to assure a secure bond to shells 28 and 29, respectively.
  • shells 28 and 29 may be extruded continuously in the shape shown and then cut to any desired length.
  • Each of shells 28 includes a rectangular back portion 33 and two side portions 34 and 35 which extend at angles from the side edges of back portion 33.
  • Shell 28 further comprises flanges 36 and 37 which extend outwardly from back 33, parallel but spaced from sides 34 and 35, respectively, to define narrow slots 38 and 39.
  • the ends 40 and 41 of flanges 36 and 37 are bent through an angle of 90 so as to extend towards each other, ends 40 and 41 being coplanar with each other and with the ends of sides 34 and 35.
  • approximately twothirds of the distance between back 33 and ends 40 and 41, flanges 36 and 37 have short dog-legs 42 and 43, respectively, for reasons which will appear more fully hereinafter.
  • Shell 29 includes a base portion 44 which is bent through an angle of at the exact center thereof to form an apex 45 and two sides 46 and $7.
  • the free ends 48 and 49 of sides 46 and 47, respectively, are bent through angles of 30 relative to sides 46 and 47, respectively, so that they are parallel to each other, as shown.
  • the spacing between ends 48 and 49 is exactly equal to the spacing between slots 38 and 39 in shell 28 and the lengths of ends 48 and 69 are slightly smaller than the depths of slots 38 and 39.
  • ends 48 and 49 of shell 29 extend into slots 38 and 39, respectively, of shell 28.
  • sides 46 and 47 of shell 29 include outwardly projecting cars 50 and 51, respectively, at
  • Each of shells 29 further. includes flanges 54 and 55 which extend inwardly from the inner surfaces of sides 46 and 47, respectively, thereof. Flanges 54 and 55 are coplanar and are spaced from ends 40 and 41, respectively, of shell 28 by an amount which is slightly greater than the desired width of inlet openings 24. The ends 56 and 57 of flanges 54 and 55, respectively, are bent through an angle of 60 so as to extend parallel to sides 46 and 47, respectively, towards apex 45. The spacing between ends 56 and 57 and sides 46 and 47, respectively, as well as the spacing between ends 40 and 41 and back 33 is determined by the thickness desired for sound deadening material 30 and 31, respectively.
  • each of shells 29 has a plurality of elongated openings 24 in each ofsides 46 and 47, between ears 50 and 51 and flanges 54 and 55, respectively.
  • the length, width, location, and spacing between openings 24 will be discussed more fully hereinafter. At the present time, openings are not formed in shell29.
  • shell 29 define the areas of shells 28 and 29 which are to be lined with sound deadening materials and 31, respectively.
  • any suitable sound deadening material may be used al though a polyurethane closed cell foam is highly effective and most desirable.
  • a polyurethane closed cell foam may be applied to shells 28 and 29 in the manner described, in copending U. 5.
  • shells 28 and 29 may be positioned on their backs, with the sides to be lined with foam facing upwardly, and passed beneath a plurality of spray nozzles which inject a polyurethane foam, in liquid form, thereon. Shells 28 and 29 would then be passed beneath conveyor belts which permit rising of the foam to the desired shape.
  • a flat conveyor belt resting on top of ends and 41 of flanges 36 and 37, respectively, will permit the foam to fill the area defined by back 33, flanges 36 and 37, and ends 40 and 41 thereof.
  • a triangular conveyor belt resting on top of ends 56 and 57 of flanges 54 and 55, respectively, and having a suitable cross-sectional shape would be required to permit the foam to line the inner surfaces of sides 46 and 47,from flange 54 to flange 55.
  • the foam would have a suitable bonding agent included therein so as to form a rigid, unitary structure with shells 28 and 29.
  • cells 20 may be installed in any suitable manner. For example, if cells 20 are to be used along a roadway 1 1, as shown in FIG. 1, cells 20 may be formed in 4 or 6 foot lengths and mountee a short distance from the side of roadway 11. The cells 20 may also be stacked, one above the other, to any desired height.
  • a suitable mounting technique would be to support, in any suitable manner, first and second horizontal, vertically spaced angles 13 and 14 along the side of roadway 11 with first sides 16 and 17 of angles 13 and 14, respectively, coplanar and with second sides 18 and 19 of angles 13 and 14, respec tively, parallel and spaced by an amount slightly greater than the length of cells 20. Thereafter, cells 20 may be positioned between angles 13 and 14, with sides 21 thereof resting against sides 16 and 17 of angles 13 and 14, respectively. A plurality of sheet metal screws 8 may then be extended through a plurality of holes 9 formed in sides 16 and 17 of angles 13 and 14, respectively, and into backs 33 of sides 21 of cells 20. This simple procedure permits rapid and efficient assembly of barrier 10 along the side of roadway 11.
  • side 18 of angle 13 serves as a cover to prevent various forms of environmental precipitation from getting into cells 20.
  • precipitation finds its way into cells 20, it will be drained therefrom via the space between the bottom of cells 20 and side 19 of angle 14.
  • the improvement in noise attenuation performance of sound barrier 10 is attributable to the interaction of several phenomena.
  • the exterior walls of sides 22 and 23 of cells 20 act as multiple inverse-acting acoustic horns which focus the sound en.- ergy toward openings 24 in cells 20 and 21.
  • sound or noise from a fixed or moving source produces successive waves 58 of compressed air which advance toward barrier 10. These waves undergo further compression as they travel along sides 22 and 23 between each set of cells 20. In other words, as a first wave enters the constricting area just beyond apices 45, there will be some scattering of energy.
  • the acoustic horns are essentially transformers, acting more efiiciently than the oscillating mass alone because the horn cre-
  • the compressed air which serves as the media for sound energy propagation is now diverted from a high pressure zone, at each opening 24, into the adjacent cells 20, which are at a lower pressure, rapidly expanding within cells 20, thereby dissipating additional energy.
  • the opposing waves 59 of compressed air flowing within each chamber 20 now generate turbulent air swirls which produce additional energy dissipation.
  • the swirling air patterns within each cell 20 impact against sound deadening material 30 and 31, dissipating still additional sound energy.
  • Additional wavefronts 59 of compressed air entering cells 20 recompress the preceeding wavefronts, producing additional energy losses.
  • the openings in sides 22 and 23 of cells 20 are a second phenomenon which contributes to the improvement in noise attenuation performance of sound barrier 10.
  • the compressed, expanded, and recompressed sound waves within each cell 20 now respirate through outlet openings 25 in apices 45 of cells 20 to a low pressure zone immediately in front of each apex 45. More specifically, when the successive waves 58 of compressed air reach apices 45 of cells 20, they are broken up and directed along sides 22 and 23, betweeneach pair of cells 20. This has the effect of creating a partial vacuum adjacent each apex 45, which partial vacuum draws the air within cells 20 out through openings 25.
  • the compressed air which serves as the media for sound energy propagation is now again diverted from a high pressure zone, within cells 20, adjacent openings 25, back into the atmosphere, which is at a significantly lower pressure, rapidly expanding and dissipating additional energy. Furthermore, the wavefronts 60 exiting from openings 25 propagate in a direction opposed to the incoming waves 58 which, by molecular impact, cause additional energy dissipation.
  • the first wavefronts 58 impinging upon sound barrier 10 are substantially reduced in en ergy level and a substantial portion of the remaining energy level is directed back upon the incoming sound energy, thereby decreasing the level of such sound energy before it even reaches barrier 16
  • the new wavefronts, which have now been decreased in magnitude, are recirculated through cells 20, as described previously,-
  • each of sides 21, 22, and 23 of cells may be approximately 4 inches wide and siots 15 may be oneeighth inch wide. Openings 24 may be 6 inches long and one-quarter inch wide and spaced longitudinally by 1 /2 inches. Such a configuration has been found to pro prise superior operating characteristics.
  • slots 15 are necessary since they permit air circulation between each pair of cells 20, so as to prevent unwanted air circulation or air pressure build-up near inlet openings 24. Slots 15 also subdue diaphragm-like vibrations of the rear walls 33 of cells 20, which otherwise would act as secondary noise sources.
  • outlet openings 25 may be 6 inches long by three thirty-second inches wide and may be spaced longitudinally by 1 foot. With such dimensions, the ratio of the combined area of inlet openings 24 to the combined area of outlet openings 25 is 10.77 to 1 and this ratio has been found through tests to be highly effective. In other words, the ratio of the combined area of inlet openings 24 in each cell 20 to the combined area of outlet openings 25 should be at least approximately 10 to 1.
  • a sound barrier 10 which offers the potential for eliminating not only the disadvantages of conventional highway noise barriers but also for solving the problems inherent in sound barriers using Helmholtz resonating chambers and inverseacting acoustic horns.
  • Sound barrier it) is not only inexpensive, but is capable of reflecting, absorbing, and converting sound energy to substantially lower levels under all atmospheric conditions. With sound barrier 10, effective sound reduction is only slightly dependent upon barrier height and barrier heights of only 6 feet are capable of achieving attenuations of 20 dB and more.
  • Sound barrier M) blends aesthetically with the surrounding landscape and a motorist in vehicle 12 is not given the impression that he is captured within a tunnel since at freeway speeds, sound barrier 10 is visually transparent.
  • sound barrier 10 is not effected by wind currents and other atmospheric conditions and operates as well in the field as in a testing chamber.
  • the wind currents which are focused by walls 22 and 23 towards openings 24 in cells 20 respirate not only through slots 15 but also through cells 2% via inlet and outlet openings 24 and 25, respectively.
  • these wind currents do not modify or reduce the energy cancellation properties of barrier 10.
  • each cell 20 acts as a sound energy exchanger, receiving air and sound waves and redirecting them, the latter in decreased form, in a definite, prescribed direction.
  • Cells 20 are thus distinguishable from Helmholtz chambers which function only as resonators.
  • cells 20 are shown having a length of approximately 4 feet and as being mounted vertically along the side of roadway 11.
  • a sound barrier generally designated 70
  • Barrier 70 consists of a plurality of hollow, wedge-shaped, energy dissipating cells 72 which are identical in construction and operation to cells 20. 5
  • each of cells 73 is quite long and cells 73 are mounted horizontally in parallel, side-by-side, spaced relationship along the sides of runway 71.
  • Cells 73 may be mounted with first sides coplanar or may be mounted with first sides positioned along an arcuate supporting surface 74. This latter configuration has the advantage of redirecting some of the incident sound energy upward and not back towards aircraft 72.
  • Other configurations and orientations of energy dissipating cells constructed in accordance with the teachings of I5 the present invention will be apparent to those skilled in the art.
  • a sound barrier comprising:
  • a plurality of hollow, energy dissipating cells each having a triangular cross-section, mounted in parallel, side-by-side, spaced relationship with first sides of all of said cells being coplanar or aligned with a continuous, arcuate surface and the remaining two sides of all of said cells extending in the same direction, towards a source of sound;
  • each of said cells having a plurality of inlet openings in each of said remaining two sides thereof, said inlet openings being spaced along the edges of said two sides which are adjacent said first side;
  • each of said cells further having at least one elongated outlet opening along the apex thereof defined by the intersection of said two sides, the combined area of said plurality of inlet openings in each cell being substantially greater than the area of said elongated outlet opening in each cell.
  • a sound barrier according to claim 1 wherein the spacing between adjacent cells is substantially smaller than the width of said first sides thereof.
  • a sound barrier according to claim 8 wherein said sound deadening material is polyurethane closed cell foam.
  • a sound barrier according to claim 6 wherein said sound deadening material is polyurethane closed cell foam.
  • each of said cells consists of two subassemblies, a first generally rectangular subassembly from which said first side is formed and a'second generally triangular subassembly from which said remaining two sides are formed, said first and second subassemblies including means for forming an interlocking connection therebetween.
  • each of said subassemblies comprises a thin outer shell of structurally rigid material and an inner lining of sound deadening material.
  • said shell of said first subassembly comprises:
  • first and second flanges which extend outwardly from said back portion, parallel to and spaced from said side portions to define narrow slots therebetween; and wherein said shell of said second subassembly comprises:
  • a sound barrier according to claim 13 wherein I said means for forming an interlocking connection between said subassemblies comprises:
  • each outwardly projecting ear and each inwardly projecting ear being equal to the distance between said dog-legs and the ends of said flanges whereby said outwardly projecting ears rest on the ends of said side portions of said first subassembly and said inwardly projection ears afe captured beneath said dog-legs in said flanges of said first subassembly.
  • first and second flanges extending inwardly from the inner surfaces of said sides thereof, said flanges being coplanar and spaced from said ends of said sides by an amount which is slightly greater than the width of said inlet openings, said lining of sound deadening material of said second subassembly extending along the inner surfaces of said sides of said shell, between said flanges thereof.

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US8789652B2 (en) 2009-02-06 2014-07-29 Sonobex Limited Attenuators, arrangements of attenuators, acoustic barriers and methods for constructing acoustic barriers
US20160356036A1 (en) * 2015-06-03 2016-12-08 Epic Metals Corporation Tunable Specular Acoustic Deck
US9607600B2 (en) 2009-02-06 2017-03-28 Sonobex Limited Attenuators, arrangements of attenuators, acoustic barriers and methods for constructing acoustic barriers
US20180171563A1 (en) * 2016-12-19 2018-06-21 Evonik Röhm Gmbh Transparent sound-absorbing noise protection element
US10105890B2 (en) 2006-01-31 2018-10-23 Kevin P. Kelly Modular wall system
WO2018235974A1 (en) * 2017-06-22 2018-12-27 Ketech Co., Ltd. AIR PASSING SOUNDPROOF PANEL AND AIR PURIFYING SOUNDER WALL USING THE PANEL
US10580396B1 (en) * 2017-04-07 2020-03-03 The United States Of America As Represented By The Secretary Of The Navy Acoustically stiff wall
US20210372060A1 (en) * 2020-05-27 2021-12-02 Mute Wall Systems, Inc. Sound Dampening Barrier Wall
US11555280B2 (en) * 2020-09-29 2023-01-17 Toyota Motor Engineering & Manufacturing North America, Inc. Sound absorbing structure having one or more acoustic scatterers for improved sound transmission loss

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US4136856A (en) * 1974-03-25 1979-01-30 Custom Automatic Sound attenuating structure
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US4050538A (en) * 1975-06-05 1977-09-27 Societe D'etudes Generales De Communications Industrielles Et Civiles-Segic Noise reducing screen
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FR2382736A2 (fr) * 1977-03-03 1978-09-29 Bridgestone Tire Co Ltd Dispositif de reduction de bruit
FR2408888A1 (fr) * 1977-11-10 1979-06-08 Elektronikcentralen Structure d'absorption du son
US4244439A (en) * 1977-11-10 1981-01-13 Elektronikcentralen Sound-absorbing structure
US4214411A (en) * 1978-01-16 1980-07-29 The Fanwall Corporation Panel and joint system and transparent acoustic barriers employing same
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US4228867A (en) * 1979-02-02 1980-10-21 Lockheed Corporation Noise barrier
US4262883A (en) * 1979-11-13 1981-04-21 Feeken Ronald H Fence construction for livestock
US4352484A (en) * 1980-09-05 1982-10-05 Energy Absorption Systems, Inc. Shear action and compression energy absorber
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FR2630469A1 (fr) * 1988-04-25 1989-10-27 Val Marcel Structure autoporteuse destinee a la realisation d'ecrans antibruits isolants et absorbants, a correction acoustique variable et son procede de realisation
US5591904A (en) * 1993-10-21 1997-01-07 Rheinhold & Mahla Ag Apparatus for diminishing intake vortexes in jet engines
US5678364A (en) * 1994-07-20 1997-10-21 Bridgestone Corporation Soundproof wall
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US10105890B2 (en) 2006-01-31 2018-10-23 Kevin P. Kelly Modular wall system
US8789652B2 (en) 2009-02-06 2014-07-29 Sonobex Limited Attenuators, arrangements of attenuators, acoustic barriers and methods for constructing acoustic barriers
US9607600B2 (en) 2009-02-06 2017-03-28 Sonobex Limited Attenuators, arrangements of attenuators, acoustic barriers and methods for constructing acoustic barriers
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US9932736B2 (en) * 2015-06-03 2018-04-03 Epic Metals Corporation Tunable specular acoustic deck
US20160356036A1 (en) * 2015-06-03 2016-12-08 Epic Metals Corporation Tunable Specular Acoustic Deck
US20180171563A1 (en) * 2016-12-19 2018-06-21 Evonik Röhm Gmbh Transparent sound-absorbing noise protection element
US10580396B1 (en) * 2017-04-07 2020-03-03 The United States Of America As Represented By The Secretary Of The Navy Acoustically stiff wall
WO2018235974A1 (en) * 2017-06-22 2018-12-27 Ketech Co., Ltd. AIR PASSING SOUNDPROOF PANEL AND AIR PURIFYING SOUNDER WALL USING THE PANEL
US20210372060A1 (en) * 2020-05-27 2021-12-02 Mute Wall Systems, Inc. Sound Dampening Barrier Wall
US12006643B2 (en) * 2020-05-27 2024-06-11 Mute Wall Systems, Inc. Sound dampening barrier wall
US11555280B2 (en) * 2020-09-29 2023-01-17 Toyota Motor Engineering & Manufacturing North America, Inc. Sound absorbing structure having one or more acoustic scatterers for improved sound transmission loss

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