EP2394033B1 - Silencieux avec inserts hélicoïdaux - Google Patents

Silencieux avec inserts hélicoïdaux Download PDF

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Publication number
EP2394033B1
EP2394033B1 EP10704784.7A EP10704784A EP2394033B1 EP 2394033 B1 EP2394033 B1 EP 2394033B1 EP 10704784 A EP10704784 A EP 10704784A EP 2394033 B1 EP2394033 B1 EP 2394033B1
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EP
European Patent Office
Prior art keywords
gas
helical
sound
gas channel
sound absorber
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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.)
Not-in-force
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EP10704784.7A
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German (de)
English (en)
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EP2394033A1 (fr
Inventor
Jörg MELCHER
Daniel Fingerhut
Christian Melcher
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Deutsches Zentrum fuer Luft und Raumfahrt eV
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Deutsches Zentrum fuer Luft und Raumfahrt eV
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Publication of EP2394033A1 publication Critical patent/EP2394033A1/fr
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Publication of EP2394033B1 publication Critical patent/EP2394033B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/081—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling by passing the gases through a mass of particles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/089—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using two or more expansion chambers in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/12—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using spirally or helically shaped channels

Definitions

  • the invention relates to a silencer with at least one gas channel through which a gas flows and the features of the preamble of the independent patent claim 1.
  • the flowing gas should be able to pass through as unhindered as possible.
  • the flowing gas propagating sound waves which are to be understood here as any fast pressure fluctuations of the flowing gas, but should be as damped as possible.
  • mufflers In addition to silencers, in which sound waves energy is removed by gas friction in porous material and converted into heat, are also known mufflers that absorb sound dynamically. In engineering they are referred to as acoustic absorbers, in physics as dynamic absorbers. These are resonance systems that absorb sound occurring at their natural frequency very well and can dissipate in the sequence. Examples include so-called hole or Helmholtz resonators. It is also part of the measures known in the field of dynamic sound absorbers to build up acoustic resonators with the aid of one or more cross-sectional jumps, ie changes in the diameter of the pipe delimiting a gas duct. As a result, however, the flow resistance for the gas flowing through the muffler gas is drastically increased.
  • a muffler for internal combustion engines having the features of the preamble of independent claim 1 is known.
  • a helical installation is provided in a gas channel through which a gas flows, which gives a helical course to an interior region of the gas channel.
  • the sound is to be reduced at the helical surfaces of the helical installation by reflection and scattering and subsequent absorption in the channel wall of the gas channel and also prevented due to the so-called cut-off effect on its propagation.
  • the gas channel is surrounded by an annular channel which communicates via perforations with the gas channel and is arranged in the sound absorption material, such as ceramic wool.
  • a vote on one or more main sound frequencies, ie a particularly high efficiency at these main sound frequencies is not possible in the known muffler.
  • a device for reducing pressure pulsations in fluid-carrying piping systems is known.
  • a throttle body is arranged in a line of the conduit system, which has a helical coil whose screw axis is aligned in the propagation direction of the pressure pulsations in the conduit.
  • the pressure pulsations interact with the helical coil.
  • This may be a passive interaction under elastic shaping of the helical coil.
  • the helical coil can be activated actively.
  • It can also be arranged a plurality of throttle body in the form of helical coils in a fixed distance between the throttle bodies in a row in the respective line.
  • the doctrine of DE 10 2004 006 031 A1 expressly different from that of the DE 199 32 714 A1 not on gas-carrying, but only on liquids leading piping systems.
  • An absorber for absorbing airborne sound in which an acoustic series circuit and an acoustic parallel circuit are coupled together, wherein the acoustic series circuit is a Helmholtz resonator.
  • This Helmholtz resonator consists of a hollow body with an air volume and a cross-sectional constriction as an opening.
  • the parallel circuit is also a resonator, which is realized by a parallel connection of an acoustic suspension - realized by an air volume - with an acoustic mass, which is given by the oscillating air in a neck.
  • the acoustic series circuit and the acoustic parallel circuit are tuned to the same resonant frequency.
  • the known absorber as such is not traversed by a gas, but is provided to form a generally gas-tight wall in a sound-absorbing manner.
  • the temporary entry of gas into the hollow body or air volumes of the known absorber unlike a gas-flowed muffler, does not lead to any net gas flow that runs through it.
  • the GB 460,148 A discloses another muffler for internal combustion engines having the features of the preamble of independent claim 1.
  • embodiments of the known muffler which have a plurality of gas channels, which is divided by the flowing gas.
  • Helical internals may be provided inside the gas channels.
  • the helical internals may have at their ends inlet and outlet areas in which their diameter in the direction of flow of the gas steadily approaches from the inside to the wall of the gas channel and from this.
  • the slope of the helical internals of the known muffler can be variable.
  • the gas channels may also have tapers and extensions of their free cross section along their main extension direction.
  • the multiple gas channels are z. B. are used for the extinguishing superposition of sound waves, which propagate in the flowing gas.
  • a silencer having the features of the preamble of independent claim 1 is also known from US Pat. No. 3,746,126 known. Here it is proposed to provide a helical installation in front of or behind a bend in an exhaust pipe of an internal combustion engine.
  • a silencer having the features of the preamble of independent claim 1, which has a plurality of helical internals, inter alia both in closely spaced Innnenrohrabroughen as well as in annular spaces between the inner tube sections and an outer tube, is from the FR 804 593 A known.
  • the invention has for its object to provide a muffler with the features of the preamble of independent claim 1, which has a high noise attenuation compared with the flow resistance of the gas through the muffler with passive means.
  • this object is achieved by a silencer having the features of independent claim 1.
  • Preferred embodiments of the new silencer are described in the dependent claims 2 to 12.
  • the dependent claim 13 relates to preferred uses of the new silencer.
  • a Helmholtz resonator is formed in the gas channel, which is excited in the gas channel by means of at least one helical installation in a gas channel through which a gas flows, the installation an inner region of the gas channel spread the gas channel flowing gas.
  • a cavity in the flow direction of the gas is limited by opposing impedance jumps for the propagating in the gas sound waves.
  • energy is trapped by a continuous sound wave whose wavelength matches the length of the cavity, i. H. to which the Helmholtz resonator is tuned.
  • the gas channel can be free, ie have no helical installation.
  • the muffler may also have another helical installation adjacent thereto or other characteristics of the helical installation adjacent thereto.
  • the opposing impedance jumps for limiting the cavity of the Helmholtz resonator can be set not only by the termination and resumption of helical installation on both sides of the cavity, but also by opposing changes in the pitch and / or diameter of the at least one helical installation.
  • the at least one helical installation can have at least two local constrictions or at least one local expansion.
  • a constriction has - acoustically speaking - the effect of an inertial mass whose impedance becomes very high for high frequencies. In particular, the high frequencies are not allowed to pass through such a constriction.
  • a Helmholtz resonator is formed according to the invention.
  • the helical installation causes a reduced power dissipation of the gas flowing through the constrictions, by passing the gas through the constriction, thus preventing, in particular, turbulent turbulence of the gas behind the constriction.
  • An expansion acts like a spring, so it is very high-impedance at low frequencies.
  • the helical installation prevents turbulence associated with loss of the gas flowing into the expansion.
  • a Helmholtz resonator can already be formed within such an expansion between its flanks.
  • the gas channel of the new muffler may have a circular cross-sectional area which is spanned by the at least one helical installation with a two-flighted helix.
  • a circular cross-sectional area of the gas channel a single helix for the formation of the helical installation is generally inadequate, since it leaves a passage region for sound waves near its axis, which is virtually uninfluenced by it.
  • the gas channel has an annular cross-sectional area, it is sufficient if it is spanned by the helical installation with at least one helical coil.
  • the new muffler also several gas channels may be provided, to which the flowing gas is divided.
  • one of these gas passages may have a circular cross-sectional area and another of these gas passages may have an annular cross-sectional area lying around it.
  • Helmholtz resonators are typically formed by means of helical internals in all of these gas channels of the new silencer.
  • this is designed as a two-circuit resonant absorber, in which in two gas ducts, on which the flowing
  • Gas is distributed, on the same frequencies of stimulating sound waves tuned Helmholtz resonators are provided, of which the one or more Helmholtz resonators are designed in the one gas channel as an acoustic parallel circuit and the Helmholtz or the resonators in the other gas channel as an acoustic series circuit.
  • a two-circuit resonant absorber as he basically already from the DE 195 33 623 B4 is known, for the first time in a gas-flow system application in which the gas flows through the Helmholtz resonators themselves.
  • a plurality of Helmholtz resonators can also be formed one behind the other in a gas channel. This is preferred, for example, to attenuate sound waves with a particularly disturbing main sound frequency as completely as possible. In this case, all or at least several of the Helmholtz resonators arranged one behind the other are then to be matched to precisely this main sound frequency.
  • Helmholtz resonators connected in series can also be tuned to different frequencies, whereby in turn for each frequency a plurality of Helmholtz resonators can be provided.
  • the at least one helical installation of the new silencer is actively deformable.
  • this active deformability can be used to detune a Helmholtz resonator formed by means of the helical installation.
  • in the quasistatic range it is possible to vary the impedance jumps occurring at the helical installation.
  • active generation of antisound by active dynamic deformation of the helical assembly is also possible to provide an actively sound-attenuating effect in addition to the passive-absorbing function of the Helmholtz resonators.
  • the sound waves at the ends, especially at the entrance of the new muffler should not reflect unnecessary become.
  • a reflection-poor, soft impedance transition is achieved in the muffler according to the invention in that the helical installation has at least one end of the muffler an inlet or outlet region by its diameter in the flow direction of the gas steadily approaches from the inside to the wall of the gas channel or removed from this. The sound waves thus reach almost completely into the new silencer and are then selectively absorbed there.
  • the new silencer is available for all gas-flow pipes, where the gas leads unsteady pressure fluctuations and in particular sound waves.
  • Such tubes exist in internal combustion engines, heaters, such as for the exhaust air of a burner, ventilation systems and the like.
  • the new muffler can be used advantageously when the sound waves or unsteady pressure fluctuations have a fixed frequency to which the Helmholtz resonator is tunable.
  • FIG. 1 sketched muffler 1 has in a tube 2 with a wall 3 three helical internals 4, 5 and 6.
  • the helical installation 5 lies between the end-side helical internals 4 and 6 and has a same free distance 7 in the direction of the tube axis 8 of the tube 2 for each of these.
  • Each of the helical internals 4-6 consists of a twinned helix 9 twisted around the tube axis 8.
  • the diameter of the double-flighted helix 9 of the end helical internals 4 and 6 steadily increases from zero to the diameter of the tube 2.
  • the two-start helix 9 has the diameter of the tube 2, it is firmly mounted on the wall 3.
  • the double-flighted helices 9 impart a helical course to an inner region 10 of a gas channel 11 leading through the tube 2 and bounded by the wall 3 thereof.
  • each of the double-flighted helices 9 delimits two helically extending part inner regions 12 of the gas channel 8 from one another.
  • the helical internals 4-6 For a gas flow along the tube axis 8 through the gas channel 11 mean the helical internals 4-6, although an increase in the flow resistance. However, this increase in the flow resistance is relatively small.
  • Sound waves mean that the helical internals 4-6, however, a strong variation of the impedance.
  • This variation is continuous at the ends of the muffler 1 due to the continuously changing diameters of the double-flighted helices.
  • impedance jumps occur.
  • two Helmholtz resonators 13 are formed in the muffler 1, the cavities or cavities 14 correspond to the free pipe cross section along the distances 7.
  • Both Helmholtz resonators 13 are tuned by the same distances 7 to the same frequencies, which is a main sound frequency, which occurs in the gas flowing through the gas channel 11 gas. Sound waves with this main sound frequency is deprived of energy by the Helmholtz resonators 13, which is ultimately converted into heat. This is done in comparison to the efficiency of the sound attenuation only minimal impairment of the gas flow, ie with minimal flow resistance for the flowing gas.
  • the embodiment of the muffler 1 according to Fig. 2 differs from the one according to Fig. 1 in that only one Helmholtz resonator 13 is formed, in which no additional helical installation between the helical internals 4 and 6 is provided.
  • the geometric relationships in the helical internals 4 and 6 are different than in Fig. 1 in that their numbers of turns are greater and the end-side inlet or outlet areas in which the diameter of the double-flighted helices 9 continuously widens from zero to the diameter of the tube 2 are stretched longer.
  • the frequency to which the respective muffler 1 is tuned depends essentially on the length of the cavity 14 of its Helmholtz resonators 13, ie on the distance 7. This length must be adjusted so that waves standing here with the wavelength of the can train interesting main sound frequency. That is, it depends not only on the geometric distance 7 but also on the speed of sound propagation within the gas channel 10 and thus on the gas guided therefrom and its state.
  • the muffler 1 according to Fig. 3 is again essentially the same Fig. 1 , ie there is again an additional helical installation 5 available. However, the geometric data of the muffler 1 are opposite Fig. 1 varied.
  • the muffler 1 according to Fig. 4 differs from those according to the Fig. 1 and 3 again by its geometric dimensions. While so far all two-stringed Helices 9 in the helical internals 4 to 6 had the same slope, here in the helical installation 5 a strongly deviating upward slope is provided. In this way, a further Helmholtz resonator 15 may be formed, the cavity of which extends along the helical partial inner regions 12 in the region of the helical installation 5. In principle, the formation of such a further Helmholtz resonator 15 is conceivable in all helical installations 4-6.
  • the attenuation within the helical internals 4-6 at a smaller pitch of the double-flighted helices 9 for the formation of an effective resonator is quickly too large.
  • the function as a Helmholtz resonator is also hindered by the outgoing diameter of the double-flighted helices 9, because this means a flowing impedance transition and no impedance jump.
  • a flowing impedance transition does not reflect sound waves in the gas within the gas channel 11 and is therefore unsuitable for limiting the cavity of a Helmholtz resonator.
  • this flowing transition serves specifically to allow the sound waves initially to enter the silencer 1 unhindered, in order then to absorb them there.
  • the muffler 1 according to Fig. 5 shows again in all helical internals 4-6 equal slopes of the double-flighted helices 9.
  • two helical internals 5 are now provided between the end-side helical internals 4 and 6.
  • Also between these helical internals 5 is the same distance 7 as before to the helical internals 4 and 6. Accordingly, three Helmholtz resonators 13 are formed here.
  • additional Helmholtz resonators 15 may in principle also be formed in their regions.
  • the muffler 1 according to Fig. 6 has yet another central helical installation 5, so that a total of four Helmholtz resonators 13 are formed between the helical internals 4-6.
  • the pitch of the double-flighted helices 9 of the helical internals 5 is significantly smaller than in the case of the double-flighted helices 9 of the end-side helical internals 4 and 6.
  • Fig. 7 shows a muffler 1, in which on the one hand by means of a total of five central helical internals 5 between the end-side helical internals 4 and 6 six Helmholtz resonators over the free distances 7 are formed, and in the other end of the helical internals 4 and 6 abrupt, ie with full diameter of its double-flighted Helices 9 end. In this way, an impedance jump is formed at the ends of the muffler 1. Accordingly, an additional Helmholtz resonator 15 can also be formed here within each helical installation 4-6.
  • Fig. 8 outlined a muffler 1, in the tube 2 only a single helical installation 4 is provided.
  • This helical installation 4 runs at both ends of the muffler 1 with the tube axis 8 steadily decreasing diameter of its double-flighted helix 9 in order to form reflection-free transitions there.
  • the helical installation 4 and the tube 2 have three common constrictions 17.
  • the constrictions act acoustically like sluggish masses whose impedance becomes very high for high frequencies, so that the high-frequency sound waves are reflected between them.
  • muffler 1 In the embodiment of the muffler 1 according to Fig. 10 are constrictions 17 according to Fig. 8 and the expansion 19 according to Fig. 9 combined to form various Helmholtz resonators 16 and 18.
  • the gas is divided into two gas channels 21 and 22, wherein the gas channel 21 is an annular channel which extends between the tube 2 and an inner tube 23, while the gas channel 22 extends through the inner tube 23.
  • the inner regions 24 and 25 of the gas channels 21 and 22 are here each formed by helical internals 26 and 27 to screw flights. In this case, only the helical internals 27 in the inner tube 23 are necessarily double-flighted helices9.
  • the helical internals 6 in the annular gas channel 21 may also be single helices, as shown here. With the helical internals 26 and 27, Helmholtz resonators 28 and 29 are formed in both gas channels 21 and 22, but here the order of helical internals 26 and 27 and their free distances between the gas channels 21 and 22 is reversed. D. h., At the ends of the gas channel 21 are helical internals and at the ends of the gas channel 22 are free spaces. The acoustic parallel circuit forms the gas channel 22, which has the end-side free spaces. These form acoustic springs, while the helical internals 26 and 27 correspond to acoustic masses.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Claims (13)

  1. Silencieux (1) pour une onde sonore se propageant dans un gaz qui s'écoule, avec au moins un canal de gaz (11, 21, 22) traversé par un gaz, dans lequel au moins une structure hélicoïdale (4-6, 26, 27) est prévue, qui confère à une partie interne (10, 24, 25) du canal de gaz (11) une forme de vis, caractérisé en ce que, à l'aide de l'au moins une structure hélicoïdale (4-6, 26, 27), un résonateur de Helmholtz (13, 15, 16, 18, 28, 29) est formé dans le canal de gaz (11), qui comprend une cavité (14) limitée, dans la direction d'écoulement du gaz, par des sauts d'impédance contrarotatifs pour les ondes sonores se propageant dans le gaz et qui est excité par les ondes sonores se propageant dans le gaz qui s'écoule, de façon à ce que l'énergie provenant d'une onde sonore se propageant soit capturée, dont la longueur d'onde correspond à la longueur de la cavité, et en ce que la structure hélicoïdale (4) comprend, au moins à un extrémité du silencieux (1), une partie d'entrée ou de sortie dans laquelle son diamètre s'approche resp. s'éloigne progressivement, dans le sens d'écoulement du gaz, de l'intérieur vers resp. de la paroi (3) du canal de gaz (11).
  2. Silencieux (1) selon la revendication 1, caractérisé en ce que les sauts d'impédance contrarotatifs sont réalisés à l'aide de variations contrarotatives du pas et/ou du diamètre de l'au moins une structure hélicoïdale (4-6, 26, 27).
  3. Silencieux (1) selon la revendication 2, caractérisé en ce que l'au moins une structure hélicoïdale (4) comprend, en plus d'une paroi (3) du canal de gaz (11), qui l'entoure, au moins un rétrécissement (17) ou un élargissement (19) local.
  4. Silencieux (1) selon la revendication 1, caractérisé en ce qu'aucune structure hélicoïdale ne se trouve dans la cavité (14).
  5. Silencieux (1) selon au moins l'une des revendications précédentes, caractérisé en ce que le canal de gaz (11, 22) présente une surface de section transversale circulaire qui est occupée par une structure hélicoïdale (4-6, 27) avec une double hélice (9).
  6. Silencieux (1) selon au moins l'une des revendications précédentes 1 à 5, caractérisé en ce que le canal de gaz (21) présente une surface de section transversale qui est occupée par la structure hélicoïdale (27) avec au moins une spirale.
  7. Silencieux (1) selon au moins l'une des revendications précédentes, caractérisé en ce que plusieurs canaux de gaz (21, 22) sont prévus, entre lesquels se répartit l'écoulement de gaz.
  8. Silencieux (1) selon la revendication 7, caractérisé en ce que, dans tous les canaux de gaz (21, 22), des résonateurs de Helmholtz (28, 29) sont conçus avec des structures hélicoïdales (26, 27).
  9. Silencieux (1) selon la revendication 8, caractérisé en ce que, dans tous les canaux de gaz (21, 22), se trouvent des résonateurs de Helmholtz (28, 29), accordés sur des fréquences d'ondes sonores d'excitation identiques, dont au moins un est conçu comme un circuit acoustique parallèle et un est conçu comme un circuit acoustique en série.
  10. Silencieux (1) selon au moins l'une des revendications précédentes, caractérisé en ce que, dans le canal de gaz (11, 21, 22), plusieurs résonateurs de Helmholtz (13, 15, 16, 28, 29) sont disposés les uns derrière les autres.
  11. Silencieux (1) selon la revendication 10, caractérisé en ce que les plusieurs résonateurs de Helmholtz (13, 15, 16, 28, 29) sont tous accordés sur une seule fréquence sonore principale ou certaines fréquences sonores principales discrètes.
  12. Silencieux (1) selon au moins l'une des revendications précédentes, caractérisé en ce que l'au moins une structure hélicoïdale (4-6, 26, 27) peut être déformée activement, plus particulièrement par l'intégration de matériaux fonctionnels.
  13. Tuyau traversé par un gaz (2), plus particulièrement dans un moteur à combustion, un chauffage ou un dispositif de ventilation, avec un silencieux (1) selon l'une des revendications 1 à 12.
EP10704784.7A 2009-02-05 2010-02-02 Silencieux avec inserts hélicoïdaux Not-in-force EP2394033B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000645A DE102009000645B3 (de) 2009-02-05 2009-02-05 Schalldämpfer mit mindestens einem mittels helikaler Einbauten aufgebauten Helmholtz-Resonator
PCT/EP2010/051217 WO2010089283A1 (fr) 2009-02-05 2010-02-02 Silencieux présentant des éléments encastrés hélicoïdaux

Publications (2)

Publication Number Publication Date
EP2394033A1 EP2394033A1 (fr) 2011-12-14
EP2394033B1 true EP2394033B1 (fr) 2015-03-25

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EP10704784.7A Not-in-force EP2394033B1 (fr) 2009-02-05 2010-02-02 Silencieux avec inserts hélicoïdaux

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US (1) US8312962B2 (fr)
EP (1) EP2394033B1 (fr)
DE (1) DE102009000645B3 (fr)
DK (1) DK2394033T3 (fr)
WO (1) WO2010089283A1 (fr)

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FI128355B (en) * 2019-01-29 2020-03-31 Teknologian Tutkimuskeskus Vtt Oy Silencers and elements and process for making them
CN112185326B (zh) * 2020-08-25 2024-05-24 西安交通大学 一种双螺旋耦合水下吸声超表面结构
CN113539223B (zh) * 2021-07-11 2022-05-06 哈尔滨工程大学 一种亥姆霍兹吸声装置
WO2023080864A1 (fr) * 2021-11-08 2023-05-11 Metapax Akustik Muhendislik Danismanlik Egiti̇m Sanayi Ve Ticaret Anonim Sirketi Silencieux d'écoulement de métamatériau acoustique à large bande
DE202024102715U1 (de) 2024-05-24 2024-06-10 Roman W. Dahlheim Schalldämpfer für eine Schusswaffe und eine Schusswaffe

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Also Published As

Publication number Publication date
US20110308884A1 (en) 2011-12-22
DE102009000645B3 (de) 2010-07-29
DK2394033T3 (en) 2015-05-04
US8312962B2 (en) 2012-11-20
EP2394033A1 (fr) 2011-12-14
WO2010089283A1 (fr) 2010-08-12

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