EP0680031A2 - Amortisseur acoustique - Google Patents

Amortisseur acoustique Download PDF

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Publication number
EP0680031A2
EP0680031A2 EP94117818A EP94117818A EP0680031A2 EP 0680031 A2 EP0680031 A2 EP 0680031A2 EP 94117818 A EP94117818 A EP 94117818A EP 94117818 A EP94117818 A EP 94117818A EP 0680031 A2 EP0680031 A2 EP 0680031A2
Authority
EP
European Patent Office
Prior art keywords
perforated plate
molded part
resonators
openings
air
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.)
Granted
Application number
EP94117818A
Other languages
German (de)
English (en)
Other versions
EP0680031A3 (fr
EP0680031B1 (fr
Inventor
Reinhard Stief
Gerhard Dr. Müller-Broll
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of EP0680031A2 publication Critical patent/EP0680031A2/fr
Publication of EP0680031A3 publication Critical patent/EP0680031A3/fr
Application granted granted Critical
Publication of EP0680031B1 publication Critical patent/EP0680031B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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 invention relates to an air silencer, comprising a plate-shaped molded part made of polymeric material with at least two chambers, which are designed as resonators with mutually different resonance frequencies, the resonators covering the entire molded part essentially flat.
  • Such a molded part is known from DE 40 11 705 C2.
  • the known air silencer comprises an air-sound-absorbing molded part which is covered on its surface facing the sound source with a porous layer or consists of open-cell foam.
  • the resonators of the previously known molded part are designed as Helmholtz resonators, each Helmholtz resonator being provided with only one opening on the side facing the sound source.
  • the invention has for its object to further develop an air silencer of the previously known type such that broadband sound absorption is made possible and that the air silencer can be used in damp and / or clean air rooms.
  • the molded part consists of a closed-cell material that the resonators through Essentially pot-shaped protrusions are formed in the direction of the sound source, that the molded part is covered on the side facing the sound source by a perforated plate which is provided with at least two openings in the area of each chamber and that the molded part and the perforated plate are separably connected to one another are.
  • the air muffler according to the invention can be used in clean air spaces due to its design and its good performance properties, since it does not release any material particles from the molded part and / or from the perforated plate into the room air and does not absorb any moisture. This reliably prevents bacterial colonization.
  • the detachable connection of the molded part from the perforated plate for example by means of a clamping system, enables the entire air silencer to be cleaned without problems.
  • the claimed air silencer ensures a much broader band of sound absorption.
  • the proportion of the openings is matched to the chamber volume of the corresponding resonators in such a way that there is good sound absorption in a frequency range of at least 250 to 4000 Hz.
  • Air mufflers designed as Helmholtz resonators can only absorb satisfactorily in a frequency range from 750 to 1500 Hz.
  • the sound that strikes the air silencer first penetrates through the perforations in the perforated plate and excites the chamber floor and the side walls of each chamber to vibrate. Part of the energy is converted into heat by the internal friction of the molded part material. The remaining part of the energy is dampened by the vibrating air plugs in the perforations of the perforated plate.
  • a chamber of the molded part which is covered with a perforated plate with multiple perforations, enables a comparatively broadband damping of impinging Airborne sound. For example, air plugs with differing volumes oscillate within the perforations of the perforated plate.
  • the molded part consists of a closed-cell foam and the perforated plate is formed by a perforated plate made of metallic material.
  • the advantage here is that the air muffler does not absorb moisture and can therefore be used in wet or clean air rooms. The air silencer can therefore be used in the food processing industry and medical areas.
  • the production of a molded part from a closed-cell foam and a perforated plate made of metallic material is advantageous in terms of production technology and economy.
  • the molded part can be provided with resonators of the same volume which have a corresponding design, the perforated plate in the region of the protrusion each having a different number and / or shape of openings.
  • the chambers In the case of an air silencer designed in this way, the chambers have a corresponding bending stiffness.
  • the broadband absorption of airborne sound is achieved through the design of the perforated plate.
  • the volume of the air plugs within the openings differs from one another.
  • the molded part is designed with resonators of differing volumes and that the perforated plate in the region of the protrusions each has a matching or different number and / or shape of openings. It is possible to provide a uniformly perforated perforated plate which covers the molded part, which is provided with resonators of different shapes. Due to the different designs of the resonators, they can have a different bending stiffness, so that good broadband sound absorption is given in a frequency range from 250 to 4000 Hz.
  • the resonators can be designed in such a way that the chamber bottom is arranged so as to be able to oscillate relatively to the side walls of the chamber.
  • the transition area from the side walls to the chamber floor can be designed as a spring element, the spring element, starting from the side walls and the chamber floor, having a reduced, continuously merging, membrane-like, thin material thickness.
  • the spring element can be designed like a bellows.
  • Correspondingly designed chambers form a spring-mass system, in which the spring is formed by the air enclosed within the chamber and by the elastically flexible spring element which is arranged in the transition region between the side walls of the chamber and the chamber bottom.
  • the mass is formed by the relatively oscillatable chamber floor. Because the chamber floor is elastically coupled to the side walls of the chamber, an improvement in sound absorption in lower frequency ranges can be brought about. Such a construction enables sound absorption in a frequency range between 100 and 4000 Hz. Characterized in that the spring element is preferably designed like a bellows, an oscillating relative movement of the chamber bottom to the side walls of the chamber causes only a slight mechanical flexing stress, which is of particular advantage in view of the good service life of the air silencer.
  • the proportion from the sum of the areas of all openings in the perforated plate is 0.05 to 0.45.
  • the ratio of the volume of each resonator and the corresponding area of the openings is preferably 20 to 25.
  • the openings are limited in a circle and have a diameter of at most 4 mm.
  • the openings preferably have a diameter of 1 to 3 mm, the resonators being designed differently from one another. If the diameter of the openings is less than 4 mm, it is advantageous that impurities within the chambers are limited to small particles.
  • the resonators have a cross section which is widened conically in the direction of the perforated plate.
  • the molded part can be removed from the mold in a particularly simple manner due to the conical configuration of the resonators. Due to the essentially conical chambers, the running of moisture deposits is always guaranteed, so that no moisture residues, for example from cleaning the air silencer, remain inside the resonators. The moisture deposits are discharged to the outside through the perforations in the perforated plate.
  • a further enlarged frequency range for the absorption of airborne sound can be brought about in that the molded part is only partially provided with a heavy layer on the side facing away from the perforated plate.
  • the resonators, which are provided with a heavy layer, result in improved airborne sound absorption of comparatively lower-frequency vibrations.
  • the air silencer can be used as ceiling and / or wall cladding in damp and / or clean air rooms.
  • FIG. 1 an embodiment of an air silencer is shown, which consists essentially of a plate-shaped part 1 and a perforated plate 8.
  • the molded part 1 is made of a closed-cell polymeric material and comprises a plurality of chambers 2, 3 which are designed as resonators 4, 5.
  • the resonators 4, 5 have mutually different volumes and thus mutually different resonance frequencies.
  • the resonators 4, 5 are open in the direction of the sound source 6 and covered by the perforated plate 8.
  • the perforated plate 8 is provided in the area of each protrusion 7 with a plurality of openings 9, 10 in order to bring about good sound absorption in a frequency range of at least 250 to 4000 Hz in connection with the resonators 4, 5.
  • the molded part 1 and the perforated plate 8 are separably connected to one another by a clamp-shaped fastening device 12.
  • the perforated plate consists of a metallic material and is applied to the molded part under elastic prestress. In the production-related state, the perforated plate is domed in a dome-like manner, similar to the resonators. During assembly, the perforated plate 8 is transferred into a flat state under elastic deformation and is thereby tightly connected to the molded part 1.
  • FIG. 2 shows a top view of the air silencer from FIG. 1. It can be seen that the resonators 4, 5 are designed differently from one another.
  • FIG. 3 shows a section of at least two plate-shaped air silencers, which are connected to one another in the area of their circumferential boundaries by the clamp-shaped fastening device 12.
  • the clamp-shaped fastening device 12 also connects the plate-shaped molded parts 1 to the adjacent perforated plates 8.
  • the resonators 4, 5 are designed differently from one another.
  • the resonator 4 is closed by a perforated plate 8, which is penetrated by openings 9, 10 which differ from one another in shape.
  • the diameters of the openings 9, 10 are 1 to 3 mm.
  • the resonator 5 is covered by a perforated plate 8, which has a plurality of identically designed openings 9, 10.
  • the resonator 5 is designed as a spring-mass system, the side walls 13 of the chamber 3 being connected to the chamber bottom 15 by a bellows-type spring element 14 which is formed in one piece with the resonator 5.
  • the surface of the perforated plates facing the sound source has a hole percentage of 25%. On the one hand, this results in good sound absorption in a wide frequency range and, on the other hand, the shape of the entire air silencer is sufficiently large.
  • FIG. 4 shows an exemplary embodiment of one, similar to the exemplary embodiment from FIG. 3.
  • the resonator 4 is provided on the side facing away from the sound source 6 with a heavy layer 11 for absorbing lower-frequency vibrations in the range up to 500 Hz.
  • the resonator 5 is provided with a chamber base 15 coupled from the side walls 13 by a spring element 14.
  • the ratio of the volume of the resonators 4, 5 and the corresponding areas of the openings 9, 10 is 22 in these exemplary embodiments.
  • the air silencers from FIG. 4 are designed as ceiling cladding provided and attached to an abutment 16 by a bracket-shaped fastening device.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Duct Arrangements (AREA)
  • Obtaining Desirable Characteristics In Audible-Bandwidth Transducers (AREA)
  • Building Environments (AREA)
  • Exhaust Silencers (AREA)
EP94117818A 1994-04-27 1994-11-11 Amortisseur acoustique Expired - Lifetime EP0680031B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4414566A DE4414566C2 (de) 1994-04-27 1994-04-27 Luftschalldämpfer
DE4414566 1994-04-27

Publications (3)

Publication Number Publication Date
EP0680031A2 true EP0680031A2 (fr) 1995-11-02
EP0680031A3 EP0680031A3 (fr) 1995-11-15
EP0680031B1 EP0680031B1 (fr) 1999-06-16

Family

ID=6516487

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94117818A Expired - Lifetime EP0680031B1 (fr) 1994-04-27 1994-11-11 Amortisseur acoustique

Country Status (4)

Country Link
US (1) US5587564A (fr)
EP (1) EP0680031B1 (fr)
JP (1) JP2986711B2 (fr)
DE (1) DE4414566C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5905234A (en) * 1994-08-31 1999-05-18 Mitsubishi Electric Home Appliance Co., Ltd. Sound absorbing mechanism using a porous material
ITRA20100013A1 (it) * 2010-05-04 2011-11-05 Simone Meneghel "pannello fonoisolante frangi-onda"

Families Citing this family (42)

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JP2848587B2 (ja) * 1995-10-23 1999-01-20 株式会社神戸製鋼所 吸音性制振形材
GB9522724D0 (en) * 1995-11-06 1996-01-10 Acts Ltd A noise attenuator for an induction system or an exhaust system
DE19620375A1 (de) * 1996-05-21 1997-11-27 Polymer Chemie Gmbh Schalldämmendes und -dämpfendes Bauteil
TW345603B (en) * 1996-05-29 1998-11-21 Gmundner Fertigteile Gmbh A noise control device for tracks
US6015026A (en) * 1997-06-06 2000-01-18 Owens-Corning Fiberglas Technology, Inc. Acoustical diffuser assembly and method of installation
DE19804567C2 (de) * 1998-02-05 2003-12-11 Woco Franz Josef Wolf & Co Gmbh Flächenabsorber für Schallwellen und Verwendung
DE29803675U1 (de) * 1998-03-03 1999-07-15 M. Faist GmbH & Co KG, 86381 Krumbach Schallschutzabschirmung
JP2000330571A (ja) * 1999-05-21 2000-11-30 Nok Vibracoustic Kk 吸音構造体
JP2001282249A (ja) * 2000-03-30 2001-10-12 Nok Vibracoustic Kk 吸音材
JP2002029330A (ja) * 2000-07-18 2002-01-29 Nok Vibracoustic Kk 吸音構造体
US7395898B2 (en) * 2004-03-05 2008-07-08 Rsm Technologies Limited Sound attenuating structures
PL1607544T3 (pl) * 2004-06-17 2009-08-31 Heimbach Gmbh & Co Kg Urządzenie do akustycznej izolacji wykładziny ściennej, sufitowej lub podłogowej
KR100571539B1 (ko) * 2004-06-30 2006-04-24 김배영 흡음 블록 및 그 시공 방법
KR101274509B1 (ko) * 2006-04-27 2013-06-13 마사오 스즈키 차음 장치
US7520370B2 (en) * 2006-05-17 2009-04-21 William Orlin Gudim Combination acoustic diffuser and absorber and method of production thereof
JP5326472B2 (ja) * 2007-10-11 2013-10-30 ヤマハ株式会社 吸音構造
EP2085962A2 (fr) * 2008-02-01 2009-08-05 Yamaha Corporation Structure absorbant les sons et composant de véhicule doté de propriétés absorbant les sons
US20090223738A1 (en) * 2008-02-22 2009-09-10 Yamaha Corporation Sound absorbing structure and vehicle component having sound absorption property
JP5194972B2 (ja) * 2008-04-09 2013-05-08 トヨタ紡織株式会社 防音材
JP5245641B2 (ja) * 2008-08-20 2013-07-24 ヤマハ株式会社 吸音構造体
DE102009034463A1 (de) 2009-07-22 2011-02-03 Filtro Klimatechnik Gmbh Schalldämpfungskörper
US8424637B2 (en) * 2010-01-08 2013-04-23 Richard L. Lenz, Jr. Systems and methods for providing an asymmetric cellular acoustic diffuser
US9275622B2 (en) * 2011-03-29 2016-03-01 Katholieke Universiteit Leuven Vibro-acoustic attenuation or reduced energy transmission
US8752667B2 (en) * 2011-10-06 2014-06-17 Hrl Laboratories, Llc High bandwidth antiresonant membrane
WO2013098384A1 (fr) * 2011-12-31 2013-07-04 Saint-Gobain Performance Plastics Chaineux Motif optimisé d'une couche antivibratoire pour des constructions de murs, de planchers et de plafonds
US8474574B1 (en) * 2012-02-29 2013-07-02 Inoac Corporation Sound absorbing structure
US11021870B1 (en) * 2013-03-14 2021-06-01 Hrl Laboratories, Llc Sound blocking enclosures with antiresonant membranes
WO2014185271A1 (fr) * 2013-05-16 2014-11-20 株式会社トヨックス Élément à rayonnement et membre de conduction thermique
US8857563B1 (en) 2013-07-29 2014-10-14 The Boeing Company Hybrid acoustic barrier and absorber
US8869933B1 (en) * 2013-07-29 2014-10-28 The Boeing Company Acoustic barrier support structure
WO2016026424A1 (fr) * 2014-08-20 2016-02-25 The Hong Kong University Of Science And Technology Dispositif de protection acoustique absorbant les vibrations
GB201415874D0 (en) * 2014-09-08 2014-10-22 Sonobex Ltd Acoustic Attenuator
TWI625446B (zh) 2015-06-18 2018-06-01 德克薩斯大學體系董事會 用於抑制來自液體中的源的聲能的共振器、共振器陣列和雜訊消減系統
US9630575B2 (en) * 2015-09-30 2017-04-25 GM Global Technology Operations LLC Panel assembly with noise attenuation system
EP3550558B1 (fr) * 2016-11-29 2021-09-15 FUJIFILM Corporation Structure d'insonorisation
JP6636471B2 (ja) 2017-02-16 2020-01-29 株式会社ニフコ 吸音体、および、吸音構造
US10741159B2 (en) 2017-09-10 2020-08-11 Douglas Peter Magyari Acoustic-absorber system and method
US12403034B2 (en) 2019-01-31 2025-09-02 Flotherm, Inc. Sleeve-based body temperature regulation
JP2019194743A (ja) * 2019-08-19 2019-11-07 株式会社リコー 電気機器
DE102019128209B4 (de) * 2019-10-18 2023-02-02 Daniel Mohr Schallabsorbierende Vorrichtung mit Noppenfolienverbund und Verwendung
EP4094251B1 (fr) 2020-01-21 2025-12-17 ADBM Corp. Atténuation simultanée de hautes fréquences et amplification de basses fréquences de sons sous-marins
US12502308B2 (en) 2021-07-01 2025-12-23 Flotherm, Inc. Flexible heating pads

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5905234A (en) * 1994-08-31 1999-05-18 Mitsubishi Electric Home Appliance Co., Ltd. Sound absorbing mechanism using a porous material
US6109388A (en) * 1994-08-31 2000-08-29 Mitsubishi Electric Home Appliance Co., Ltd. Sound absorbing mechanism using a porous material
ITRA20100013A1 (it) * 2010-05-04 2011-11-05 Simone Meneghel "pannello fonoisolante frangi-onda"

Also Published As

Publication number Publication date
JP2986711B2 (ja) 1999-12-06
JPH0844370A (ja) 1996-02-16
EP0680031A3 (fr) 1995-11-15
EP0680031B1 (fr) 1999-06-16
DE4414566A1 (de) 1995-11-02
US5587564A (en) 1996-12-24
DE4414566C2 (de) 1997-11-20

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