WO1999052324A1 - Dispositif acoustique ayant recours a l'action d'une onde de flexion - Google Patents

Dispositif acoustique ayant recours a l'action d'une onde de flexion Download PDF

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Publication number
WO1999052324A1
WO1999052324A1 PCT/GB1999/000848 GB9900848W WO9952324A1 WO 1999052324 A1 WO1999052324 A1 WO 1999052324A1 GB 9900848 W GB9900848 W GB 9900848W WO 9952324 A1 WO9952324 A1 WO 9952324A1
Authority
WO
WIPO (PCT)
Prior art keywords
acoustic device
acoustic
area
panel
bending
Prior art date
Application number
PCT/GB1999/000848
Other languages
English (en)
Inventor
Henry Azima
Original Assignee
New Transducers Limited
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
Priority to NZ506731A priority Critical patent/NZ506731A/xx
Priority to EP99910539A priority patent/EP1068770B1/fr
Priority to EA200001016A priority patent/EA003215B1/ru
Priority to HU0102859A priority patent/HUP0102859A3/hu
Priority to PL99343115A priority patent/PL343115A1/xx
Priority to IL13831299A priority patent/IL138312A0/xx
Priority to AT99910539T priority patent/ATE294492T1/de
Application filed by New Transducers Limited filed Critical New Transducers Limited
Priority to KR1020007011016A priority patent/KR20010042428A/ko
Priority to BR9909901-2A priority patent/BR9909901A/pt
Priority to CA002326161A priority patent/CA2326161A1/fr
Priority to GB0020986A priority patent/GB2350008B/en
Priority to SK1455-2000A priority patent/SK14552000A3/sk
Priority to DE69924990T priority patent/DE69924990T2/de
Priority to AU29471/99A priority patent/AU746216B2/en
Priority to JP2000542953A priority patent/JP4258696B2/ja
Publication of WO1999052324A1 publication Critical patent/WO1999052324A1/fr
Priority to NO20004921A priority patent/NO20004921L/no
Priority to BG104810A priority patent/BG104810A/bg
Priority to HK01102906A priority patent/HK1032504A1/xx

Links

Classifications

    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R7/00—Diaphragms for electromechanical transducers; Cones
    • H04R7/02—Diaphragms for electromechanical transducers; Cones characterised by the construction
    • H04R7/04—Plane diaphragms
    • H04R7/06—Plane diaphragms comprising a plurality of sections or layers
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R7/00—Diaphragms for electromechanical transducers; Cones
    • H04R7/02—Diaphragms for electromechanical transducers; Cones characterised by the construction
    • H04R7/04—Plane diaphragms
    • H04R7/045—Plane diaphragms using the distributed mode principle, i.e. whereby the acoustic radiation is emanated from uniformly distributed free bending wave vibration induced in a stiff panel and not from pistonic motion
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R7/00—Diaphragms for electromechanical transducers; Cones
    • H04R7/16—Mounting or tensioning of diaphragms or cones
    • H04R7/18—Mounting or tensioning of diaphragms or cones at the periphery
    • H04R7/22—Clamping rim of diaphragm or cone against seating

Definitions

  • the invention relates to acoustic devices of the kind comprising a sound radiating member relying on bending wave action and resulting surface vibration to produce acoustic output .
  • Preferential in-board locations for transducers of active acoustic devices usefully have proportional defining coordinates.
  • Other areal distributions of bending stiffness can usefully contribute to affording other useful locations for transducers, for example substantially at geometric centres and/or at centres of mass, see International Patent Application WO98/00621 including for combining aforesaid bending wave action with further acoustically relevant 3
  • Specific embodiments of this invention additionally provide for means affording substantial restraint of bending wave vibration typically at edge, periphery or other boundary of such member or panel or acoustically active area thereof, and further typically to be at least capable of operating at least partly below coincidence frequency.
  • the wording 'substantial restraint' as used herein intentionally involves greater constraining of at least part(s) of edge(s) of the member than specifically disclosed in 097/09842, preferably as to both of edge extent (s) and effective loading, grip or effective grounding effect.
  • Resulting nominally less populous or less rich content of acoustically active/relevant resonant bending wave modes can be exemplified for simplified analogy and analysis based on equivalent simple beams with account taken of interactions, in terms of involving resonant plate modes that relative to each beam start at resonant mode frequency fl rather than fO, and further 'losing' combinational modes involving fO frequencies, but with interesting and useful effects available with respect to even-ness of spacings of directly and combinationally related natural resonant modes involving fl frequencies.
  • Ramifications are extensive and can be advantageous, including attainability of improved acoustic efficiency of energy conversion and/or often very usefully increased extents of candidate sub-areas for viable/optimal transducer location (s), at least as identified by mechanical impedance analysis as taught in co-pending International patent application PCT/GB99/00404 ; and/or typically much greater range of viability of areal shapes/proportions of said members as exemplified for isotropic bending stiffness, even at about 1:1 through to about 1:3 and more for aspect ratio (s); and/or viability of acoustic performance for panel member materials of lower intrinsic bending stiffness at least as effectively stiffened overall by contribution from edge (s) /peripheral/boundary restraint hereof; and/or 6
  • an acoustic device relying on bending wave action and capable of operating below coincidence, comprising a member affording said acoustic operation by reason of beneficial distribution of resonant modes of bending wave action therein, wherein the member has its acoustically active area at least partly bounded by means having a substantially restraining nature in relation to bending wave vibration.
  • an active acoustic device comprising a member relying on bending wave action with beneficial distribution of resonant modes thereof and beneficial location of bending wave transducer means, wherein the 7
  • member has its acoustically active area at least partly bounded by means having a substantially restraining nature in relation to bending wave vibration, and its transducer means location determined with reference to and taking account of such bounding means .
  • the entire periphery of an acoustic member hereof may be substantially restrained, or clamped; or only part (s) less than all of periphery of the member, e.g. a rectangular panel, may be restrained or clamped at one or more up to all of its side edges.
  • This can be useful as a flag- like mounting affording said substantial restraint at one side with the acoustically active area protruding therefrom, or as mounting at two sides that may be parallel and afford said substantial restraint with the acoustically active area between those mounting and restraining sides; and can facilitate the manufacture of up to fully sealed or only highly selectively vented diaphragm loudspeakers, e.g. mid/high frequency devices.
  • a fully or near-fully sealed diaphragm enables the making of a so-called infinite baffle loudspeaker to contain/control rear acoustic radiation which might otherwise be detrimental at mid to low frequencies .
  • Full substantially restraining or clamping frames also enable design of the loudspeaker assembly to be more predictable in mechanical terms, along with facilitating making a loudspeaker assembly which is relatively robust in construction (compared to a resonant panel loudspeaker in which the panel edges are substantially free or are 8
  • Substantial restraint or clamping of peripheral portion (s) or edge(s) of the acoustic member may be achieved in any desired manner, e.g. by intimately fixing the edge(s) to a strong frame or the like by means of an adhesive, or by mechanical means say involving clamping the edge(s) between frame members.
  • the desired edge restraint/clamping hereof may also be achieved by moulding techniques (such as injection moulding of plastics materials) by forming the edges of the member with integral or integrated thickened surround portions of sufficient rigidity to terminate edge movement of the acoustic member. Co-moulding of the acoustic member and thickened edge provision may be appropriate. Such moulding techniques may be particularly suitable where the acoustic member is formed as a monolith and may be readily achievable in economic manner.
  • Substantial restraint or clamping may also be used to define one acoustic member within another larger acoustic member.
  • a large acoustic panel intended for mid/low frequency operation may be moulded to include a smaller acoustic panel intended for high frequency operation and defined by medial stiffening ribs.
  • Substantial restraint or clamping action can be designed to present a mechanical termination impedance designed to control the reverberation time within the acoustic member as an aid to control of the frequency response of the member, perhaps especially at lower 9
  • Proportions of suitable resonant panel members may be as or substantially different from specific teaching of O97/09842 regarding variations on particular shapes.
  • substantially rectangular resonant panel members of substantially isotropic bending stiffness could be of aspect ratios below 1:1.5 then generally inclusive of prior teaching for substantially free edge panel members but not limited thereto as will be specifically described later herein, or greater than 1:1.5 as will also be specifically described later herein.
  • Variations for anisotropy/complex distribution of bending stiffness (es) is envisaged as above .
  • the bounding means may be at least partially about and definitive of said acoustically active area and/or about peripheral edge(s) of a panel-form member to be wholly acoustically active, typically to extent of up to 25% or more of full area boundary/peripheral edge extent, often the whole thereof .
  • Resonant panel members are generally self-supporting and would not require pre-tensioning for mechanical stability, particularly for types typical of free edge or simple edge supported use.
  • the stiffness of panel member in such cases may be as low as 0.001 Nm and the area density as small as 25g/m 2 .
  • the tensioned panel exhibits a high proportion of the properties of a tensioned film supporting bending waves and with predominantly second order or non- dispersive wave action (velocity constant with frequency) .
  • the resonant distribution may be optimised for desired acoustic behaviour by control of tensioning and boundary geometry in broad agreement with distributed mode teaching, see O97/09842.
  • a preferred modal distribution may be further augmented into action as a transducer via preferred/optimised placement of the exciter/sensor.
  • Figures 1 and 1A are exploded perspective and scrap sectional views of a resonant generally rectangular panel acoustic member 10 clamped at its edges between opposed rectangular perimeter frame members 11A,B using bolts and nuts 12A,B which may be further useful for mounting to a chassis or other mother structure;
  • Figure 2 is a scrap sectional view showing alternative edge clamping/terminating of resonant panel acoustic member 20 by edge fixing to a frame 21 by means of an adhesive 22;
  • Figures 3 and 3A are partial perspective and scrap sectional views of a plastics injection moulding 35 formed as a wall member having stiffening ribs 36 which intersect with a rectangular border 31 as a restraining edge of an acoustically active panel area 30, the border 31 also being formed by raised ribs that stiffen the edges of the operative panel area 30;
  • Figure 4 is a partial perspective view of a resonant panel acoustic member 40 stretched over a frame 41 and clamped at its edges by a surrounding clamping frame member 42;
  • Figure 4A is a partial cross-section of the embodiment of Figure 4 ; 12
  • Figure 4B is a partial cross-section similar to that of Figure 4A of alternative embodiment of resonant stretched panel acoustic member
  • Figures 5A,B are graphs showing frequency response of respective resonant panel members of A4 and A5 size, respectively, and in which the heavy line traces represent a clamped edge panel and the fine line traces represent a free or resiliently edge suspended panel;
  • Figures 6A,B and 7A,B and 8A,B are graphical representations for mechanical impedance against frequency for selected aspect ratios of clamped edge panel members
  • Figures 9A,B,C are graphical representations of related smoothed inverse mean square deviation for location of transducer means;
  • Figure 10 is a calculated quarter panel mechanical impedance plot for one clamped edge panel member;
  • Figure 11 is a graphical representation for various clamped edge panel aspect ratios
  • Figures 12A-H are measured quarter panel mechanical impedance plots for various aspect ratios
  • Figures 13A-H are related acoustic output plots as fitted to a reference value
  • Figure 14 plots maximum inverse mean square power deviation for different aspect ratios
  • Figures 15A-J are combination polar plots of acoustic output for lower resonant modes of a 1:3 aspect ratio clamped edge panel member
  • Figures 16A-D are acoustic output power comparison 13
  • the acoustic member may be and are shown as substantially rectangular and may have aspect ratios as considered preferential in W097/09842, though much wider ranges of aspect ratios will be shown to have useful potential within a general objective to obtain high modal density and even-ness of modal spread in the member .
  • Figures 4 and 4A show an embodiment of resonant acoustic member 40 stretched over a rectangular perimeter frame 41 and clamped to the rectangular perimeter frame by a clamping frame 42 to hold the acoustic member in place. Tensioning force is applied to the member 40 in the direction of arrow F.
  • the clamping frame 42 may be replaced by tensioning means 43, e.g. including tension springs 44 on a frame 45, the tensioning means being fixed to the edge of the acoustic member to stretch the member over the rectangular perimeter frame.
  • Vibration exciters may be located on the acoustic members in the embodiments of Figures 4 , 4A and 4B to excite resonance in the acoustic members to produce an acoustic output so that the acoustic members can act as loudspeakers or loudspeaker drive units.
  • These vibration exciters are not shown in Figures 4 , 4A and 4B in the interests of clarity.
  • the stiffness of a clamped edge panel of the same general kind may be lower by at least one order of magnitude, even as low as O.OOlNm.
  • the range of surface density of the said practical example of free edge panels may be 100 to 1000 g/m 2
  • the surface density of clamped edge panels may be only a fraction, even as low as
  • panel materials of relatively low rigidity can result in higher coincidence frequency, e.g. above the normal audio band, which may improve the uniformity of sound directivity from resonant loudspeaker panel. Also, less rigid panels, can afford effective augmentation of modal density in the lower registers, consequently improved 15
  • Useful variants to the fully peripherally edge/ boundary-restraint/clamping as illustrated include any effective lesser extent of substantial restraint/clamping which, for substantially rectangular panel member/active area, could be one side by omission of what is shown for three sides, or two typically parallel sides by omission of what is shown for other two sides.
  • Acoustic radiating members hereof may be excited in any of the ways suggested in W097/09842, e.g. by way of at least one inertial electro-mechanical exciter device.
  • the or each exciter device may be arranged to excite the radiating member at any suitable geometric position (s) areally of the acoustic member; whether according to principles as in W097/09842 or in accordance with mechanical impedance analysis as in PCT/GB99/00404 or as determined experimentally.
  • Such vibration exciters have been omitted from Figure 1 in the interests of clarity.
  • W097/09842 as to applicable kinds of exciters, and the positioning of such exciters may be as determined in accordance with the same principles as taught in W097/09842 and/or PCT/GB99/00404 , usually with difference available for actual locations compared with WO97/09842.
  • Figures 6A,B and 7A, B and 8A,B for mechanical impedance with frequency for panel members of selected aspect ratios and isotropic as to bending stiffness are accompanied by graphical representations of Figures 9A, B, C for smoothed mechanical impedance as measured by inverse square of mean standard deviation for location of particular promising transducer locations.
  • Precisely calculated favourable aspect ratios 1.160, 1.341 and 1.643 are revealed together with likewise precisely calculated preferential transducer location coordinates (0.437, 0.414), (0.385, 0.387) and (0.409, 0.439), respectively.
  • Figure 10 is a calculated quarter- panel mechanical impedance plot for the aspect ratio 1.16 and shows substantial extent of areas promising for transducer location, even two such separate areas (cross- hatched) .
  • Figure 11 gives comparison of such preferential clamped edge aspect ratios and transducer locations, including further for aspect ratio 1.138. 17
  • the first effective resonant mode frequency for a fully edge-clamped resonant panel member effectively requires contribution by the first resonant mode attributable to the shorter edge length, i.e. the first combination mode for plate vibration action for the two series (fx x , fx 2 :...fx n ) and (fyi, fy 2 ... fy m ) for the edge-parallel axes x,y as represented by the resonant mode spectrum equation: 19
  • FIGS. 15A-J are combination polar plots for one resonant panel member of aspect ratio 1:3 for the lower resonant mode frequencies, respectively; and in each case show landscape (solid) and portrait (dashed) planes, i.e. with longer dimension horizontal or vertical, respectively.
  • the radiation patterns are significantly different, that in the plane of the smaller length being generally smoother, and that in the plane of the longer length being more diffuse.
  • Design options include acceptability of higher frequency of lowest resonant mode, as directly dependent for any particular panel member structure on aspect ratio; acceptability of directionality where panel member vibration is markedly different in different axial directions; consequentially different power smoothness in corresponding radiation planes; related selection of orientation or attitude of the panel member as 21
  • the panel member of Figure 16A comprises 0.05mm thick black glass skins on 4mm thick Aluminium honeycomb, resulting in substantially isotropic bending stiffness of 12.26 Newtonmetres, mass density of 0.76 Kilogram/square metre, and coincidence frequency of 4.6kHz.
  • the panel member of Figure 16B comprises 0.102mm thick black glass skins on 1.8mm thick Rohacell core, resulting in substantially isotropic bending stiffness of 2.47 Newtonmetres, mass density of 0.60 Kilogram/square metre, and coincidence frequency of 9.1kHz.
  • the panel member of Figure 16C comprises 0.05mm thick MelinexTM skins on 1.5mm Rohacell core, resulting in substantially isotropic bending stiffness of 0.32 Newtonmetre, mass density of 0.35 Kilogram/square metre, and coincidence frequency of 19.2kHz.
  • These panel members are all of similar aspect ratio between 1.13 and 1.14 and driven with like exciters of 13mm active diameter and input impedance of 8 ohms.
  • Each had acoustic power output measured with all panel edges free to vibrate for resonant bending wave action of the panels, and with all edges clamped against such vibration.
  • Figures 16A-C show that clamping achieves substantial increase in acoustic output power below coincidence frequency, though not above, so there is greater beneficial 22
  • the panel members for Figures 16D-E are of the same stiffest structure as Figure 16A, but of larger sizes, namely 360mm x 315mm and 545mm x 480mm, respectively compared with 260mm x 230mm for Figures 16A to D; and there is confirmation of full clamping producing improved acoustic output power from coincidence frequency down to the lowest resonant mode frequency of the panel member concerned specifically to about 400Hz for the smallest panel members ( Figures 16A-C) and lower for the larger and largest panel members. It is also worth noting that the larger the panel members the closer the mode shapes for given frequency approximate to a sine wave.

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  • Engineering & Computer Science (AREA)
  • Multimedia (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Signal Processing (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)
  • Piezo-Electric Transducers For Audible Bands (AREA)
  • Surface Acoustic Wave Elements And Circuit Networks Thereof (AREA)
  • Obtaining Desirable Characteristics In Audible-Bandwidth Transducers (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
  • Toys (AREA)
  • Respiratory Apparatuses And Protective Means (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)

Abstract

Ce dispositif acoustique comporte un élément reposant sur l'action d'une onde de flexion avec répartition avantageuse des modes résonnants de celle-ci. La région active du point de vue acoustique de cet élément est, au moins en partie, encadrée par des moyens de nature sensiblement restrictive relativement à la vibration de l'onde de flexion. Le dispositif est susceptible de fonctionner, le cas échéant, en dessous ou au-dessus de la fréquence de coïncidence et ce, pour un dispositif acoustique actif dont les structures de transduction d'onde de flexion sont avantageusement situées, cet emplacement étant déterminé en tenant compte de l'encadrement.
PCT/GB1999/000848 1998-04-02 1999-03-30 Dispositif acoustique ayant recours a l'action d'une onde de flexion WO1999052324A1 (fr)

Priority Applications (18)

Application Number Priority Date Filing Date Title
DE69924990T DE69924990T2 (de) 1998-04-02 1999-03-30 Akustische vorrichtung nach dem biegewellenprinzip
EA200001016A EA003215B1 (ru) 1998-04-02 1999-03-30 Акустическое устройство
HU0102859A HUP0102859A3 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action
PL99343115A PL343115A1 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action
IL13831299A IL138312A0 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action
AT99910539T ATE294492T1 (de) 1998-04-02 1999-03-30 Akustische vorrichtung nach dem biegewellenprinzip
CA002326161A CA2326161A1 (fr) 1998-04-02 1999-03-30 Dispositif acoustique ayant recours a l'action d'une onde de flexion
KR1020007011016A KR20010042428A (ko) 1998-04-02 1999-03-30 굴곡파 동작의 음향장치
BR9909901-2A BR9909901A (pt) 1998-04-02 1999-03-30 Dispositivo acústico confiando sobre a ação de onda fletora
NZ506731A NZ506731A (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action
GB0020986A GB2350008B (en) 1998-04-02 1999-03-30 Acoustic device
SK1455-2000A SK14552000A3 (sk) 1998-04-02 1999-03-30 Akustické zariadenie
EP99910539A EP1068770B1 (fr) 1998-04-02 1999-03-30 Dispositif acoustique ayant recours a l'action d'une onde de flexion
AU29471/99A AU746216B2 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action
JP2000542953A JP4258696B2 (ja) 1998-04-02 1999-03-30 音響装置
NO20004921A NO20004921L (no) 1998-04-02 2000-09-29 Akustisk innretning
BG104810A BG104810A (bg) 1998-04-02 2000-09-29 Акустично устройство, основаващо се на действие на огъващо трептение
HK01102906A HK1032504A1 (en) 1998-04-02 2001-04-24 Acoustic device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9806994.1 1998-04-02
GBGB9806994.1A GB9806994D0 (en) 1998-04-02 1998-04-02 Acoustic device

Publications (1)

Publication Number Publication Date
WO1999052324A1 true WO1999052324A1 (fr) 1999-10-14

Family

ID=10829678

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1999/000848 WO1999052324A1 (fr) 1998-04-02 1999-03-30 Dispositif acoustique ayant recours a l'action d'une onde de flexion

Country Status (27)

Country Link
EP (1) EP1068770B1 (fr)
JP (1) JP4258696B2 (fr)
KR (1) KR20010042428A (fr)
CN (1) CN1143593C (fr)
AR (1) AR018832A1 (fr)
AT (1) ATE294492T1 (fr)
AU (1) AU746216B2 (fr)
BG (1) BG104810A (fr)
BR (1) BR9909901A (fr)
CA (1) CA2326161A1 (fr)
CO (1) CO4830489A1 (fr)
CZ (1) CZ300065B6 (fr)
DE (1) DE69924990T2 (fr)
EA (1) EA003215B1 (fr)
GB (2) GB9806994D0 (fr)
HK (1) HK1032504A1 (fr)
HU (1) HUP0102859A3 (fr)
ID (1) ID27055A (fr)
IL (1) IL138312A0 (fr)
NO (1) NO20004921L (fr)
NZ (1) NZ506731A (fr)
PL (1) PL343115A1 (fr)
SK (1) SK14552000A3 (fr)
TR (1) TR200002878T2 (fr)
TW (1) TW475340B (fr)
WO (1) WO1999052324A1 (fr)
ZA (1) ZA200004746B (fr)

Cited By (33)

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EP1052879A2 (fr) * 1999-05-14 2000-11-15 Harman Audio Electronic Systems GmbH Elément plat
WO2001039541A2 (fr) * 1999-11-22 2001-05-31 Harman Audio Electronic Systems Gmbh Systeme de haut-parleurs plats pour reproduction des graves
WO2001087003A2 (fr) * 2000-05-08 2001-11-15 New Transducers Limited Haut-parleur mural
WO2001087002A2 (fr) * 2000-05-08 2001-11-15 Koninklijke Philips Electronics N.V. Haut-parleur dote d'un panneau acoustique et d'un circuit d'attaque electrique
WO2002013575A1 (fr) * 2000-08-03 2002-02-14 New Transducers Limited Haut-parleur a ondes de flexion
WO2002043434A2 (fr) * 2000-11-23 2002-05-30 Harman/Becker Automotive Systems Gmbh Dispositif d'excitation electrodynamique produisant des couples de flexion
US6826285B2 (en) 2000-08-03 2004-11-30 New Transducers Limited Bending wave loudspeaker
WO2005122634A1 (fr) * 2004-06-12 2005-12-22 Puren Gmbh Élément oscillatoire d'un système de haut-parleur
US6983819B2 (en) 2002-04-02 2006-01-10 Awi Licensing Company Entertainment sound panels
US7548854B2 (en) 2002-01-31 2009-06-16 Awi Licensing Company Architectural sound enhancement with pre-filtered masking sound
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US9621994B1 (en) 2015-11-16 2017-04-11 Bongiovi Acoustics Llc Surface acoustic transducer
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US9741355B2 (en) 2013-06-12 2017-08-22 Bongiovi Acoustics Llc System and method for narrow bandwidth digital signal processing
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US9906867B2 (en) 2015-11-16 2018-02-27 Bongiovi Acoustics Llc Surface acoustic transducer
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US10639000B2 (en) 2014-04-16 2020-05-05 Bongiovi Acoustics Llc Device for wide-band auscultation
US10701505B2 (en) 2006-02-07 2020-06-30 Bongiovi Acoustics Llc. System, method, and apparatus for generating and digitally processing a head related audio transfer function
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US10959035B2 (en) 2018-08-02 2021-03-23 Bongiovi Acoustics Llc System, method, and apparatus for generating and digitally processing a head related audio transfer function
US11202161B2 (en) 2006-02-07 2021-12-14 Bongiovi Acoustics Llc System, method, and apparatus for generating and digitally processing a head related audio transfer function
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ID27055A (id) 2001-02-22
ATE294492T1 (de) 2005-05-15
AR018832A1 (es) 2001-12-12
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GB2350008A (en) 2000-11-15
EP1068770A1 (fr) 2001-01-17
EP1068770B1 (fr) 2005-04-27
CZ20003591A3 (cs) 2001-01-17
KR20010042428A (ko) 2001-05-25
HUP0102859A2 (hu) 2001-12-28
EA003215B1 (ru) 2003-02-27
JP4258696B2 (ja) 2009-04-30
NO20004921L (no) 2000-11-28
ZA200004746B (en) 2001-06-27
EA200001016A1 (ru) 2001-02-26
DE69924990T2 (de) 2006-02-23
NO20004921D0 (no) 2000-09-29
PL343115A1 (en) 2001-07-30
GB9806994D0 (en) 1998-06-03
JP2002511682A (ja) 2002-04-16
BR9909901A (pt) 2000-12-26
GB0020986D0 (en) 2000-10-11
CN1296720A (zh) 2001-05-23
IL138312A0 (en) 2001-10-31
CN1143593C (zh) 2004-03-24
AU2947199A (en) 1999-10-25
HUP0102859A3 (en) 2003-03-28
NZ506731A (en) 2003-02-28
AU746216B2 (en) 2002-04-18
CA2326161A1 (fr) 1999-10-14
TR200002878T2 (tr) 2001-01-22
TW475340B (en) 2002-02-01
BG104810A (bg) 2001-07-31
CZ300065B6 (cs) 2009-01-21
SK14552000A3 (sk) 2001-05-10
DE69924990D1 (de) 2005-06-02
GB2350008B (en) 2001-05-02

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