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EP1068770B1 - Acoustic device relying on bending wave action - Google Patents

Acoustic device relying on bending wave action Download PDF

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Publication number
EP1068770B1
EP1068770B1 EP99910539A EP99910539A EP1068770B1 EP 1068770 B1 EP1068770 B1 EP 1068770B1 EP 99910539 A EP99910539 A EP 99910539A EP 99910539 A EP99910539 A EP 99910539A EP 1068770 B1 EP1068770 B1 EP 1068770B1
Authority
EP
European Patent Office
Prior art keywords
acoustic device
acoustic
area
bending
panel
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.)
Expired - Lifetime
Application number
EP99910539A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1068770A1 (en
Inventor
Henry Azima
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.)
NVF Tech Ltd
Original Assignee
New Transducers Ltd
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 New Transducers Ltd filed Critical New Transducers Ltd
Publication of EP1068770A1 publication Critical patent/EP1068770A1/en
Application granted granted Critical
Publication of EP1068770B1 publication Critical patent/EP1068770B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • H04R7/045—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
    • H04R7/02—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
    • H04R7/16—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 pistonic action.
  • Acoustic operation is described and claimed in at least W097/09842 for both of whole panels and only parts thereof being acoustically active.
  • 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 W097/09842, preferably as to both of edge extent(s) and effective loading, grip or effective grounding effect.
  • the acoustically relevant and effective natural modes of resonant bending wave action will be different (compared with specific disclosure of WO97/09842) by reason of limiting/suppressing bending wave vibration movement at edge(s)/periphery/boundary of the member, thus effectively reducing/eliminating contributions(s) from lowest resonant mode(s) that would be active if edge(s)/periphery/boundary of the acoustically effective area of the member were as free to have bending wave distribution as specifically disclosed in WO97/09842; and reduction/substantial suppression of resonant modes involving twisting.
  • 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 f1 rather than f0, and further 'losing' combinational modes involving f0 frequencies, but with interesting and useful effects available with respect to even-ness of spacings of directly and combinationally related natural resonant modes involving f1 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 capabilities in relation to high power input transducer means for loudspeaker embodiments, all including where such restraint can afford substantial loading whether on an inertial grounding basis or as is further practical by actual fixing in a more rigid/ massive carrier or other heavy loading manner.
  • 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 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 suspended in an only lightly damping resilient manner).
  • 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 frequencies.
  • Proportions of suitable resonant panel members may be as or substantially different from specific teaching of WO97/09842 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.
  • first bending frequency For clamped panel member there is a ten-fold or thereabouts increase in first bending frequency due to the natural stiffening of the panel member when clamped. It is logical and sensible to substantially reduce the bending stiffness property to reduce the first modal frequency and before the lower frequency range. It is envisaged that 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 WO97/09842.
  • a preferred modal distribution may be further augmented into action as a transducer via preferred/optimised placement of the exciter/sensor.
  • 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 0 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 5 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 surface density of clamped edge panels may be only a fraction, even as low as 25 g/m 2 . It will, however, be appreciated that significantly stiffer and/or denser materials may be employed for acoustic panels hereof with substantial edge restraint or clamping, at least where lowest frequency performance is not a requirement. Such applications include tweeters, sirens, ultrasonic sound reproducers.
  • 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 sound quality.
  • 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.
  • 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 (crosshatched).
  • Figure 11 gives comparison of such preferential clamped edge aspect ratios and transducer locations, including further for aspect ratio 1.138.
  • the effect of this quadrature relationship is that a high aspect ratio can produce a succession of quite closely spaced resonant mode frequencies attributable to contributions by those next higher in the longer edge related series before next contribution from the next higher shorter edge related series.
  • Figure 14 plots maximum inverse mean square power deviation against aspect ratio and shows increase of power smoothness (above lowest effective resonant mode) with increasing aspect ratio peaking at about 1:3. Effectively, higher aspect ratios for boundary restrained members hereof have closer resonant mode frequencies, whereas the opposite applies to relatively free edge panels of WO97/09842.
  • Figures 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 used; and available trade-offs between power smoothness in different planes and/or of total power smoothness against similarity or otherwise of responses in landscape/portrait or azimuth/elevation planes.
  • 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.
  • 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)
  • Respiratory Apparatuses And Protective Means (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)
  • Toys (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
EP99910539A 1998-04-02 1999-03-30 Acoustic device relying on bending wave action Expired - Lifetime EP1068770B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB9806994.1A GB9806994D0 (en) 1998-04-02 1998-04-02 Acoustic device
GB9806994 1998-04-02
PCT/GB1999/000848 WO1999052324A1 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action

Publications (2)

Publication Number Publication Date
EP1068770A1 EP1068770A1 (en) 2001-01-17
EP1068770B1 true EP1068770B1 (en) 2005-04-27

Family

ID=10829678

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99910539A Expired - Lifetime EP1068770B1 (en) 1998-04-02 1999-03-30 Acoustic device relying on bending wave action

Country Status (27)

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

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US10069471B2 (en) 2006-02-07 2018-09-04 Bongiovi Acoustics Llc System and method for digital signal processing
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US9906858B2 (en) 2013-10-22 2018-02-27 Bongiovi Acoustics Llc System and method for digital signal processing
US9615813B2 (en) 2014-04-16 2017-04-11 Bongiovi Acoustics Llc. Device for wide-band auscultation
US10820883B2 (en) 2014-04-16 2020-11-03 Bongiovi Acoustics Llc Noise reduction assembly for auscultation of a body
US10639000B2 (en) 2014-04-16 2020-05-05 Bongiovi Acoustics Llc Device for wide-band auscultation
US9564146B2 (en) 2014-08-01 2017-02-07 Bongiovi Acoustics Llc System and method for digital signal processing in deep diving environment
US9638672B2 (en) 2015-03-06 2017-05-02 Bongiovi Acoustics Llc System and method for acquiring acoustic information from a resonating body
US9621994B1 (en) 2015-11-16 2017-04-11 Bongiovi Acoustics Llc Surface acoustic transducer
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Also Published As

Publication number Publication date
SK14552000A3 (sk) 2001-05-10
NZ506731A (en) 2003-02-28
DE69924990T2 (de) 2006-02-23
HUP0102859A3 (en) 2003-03-28
GB2350008B (en) 2001-05-02
CA2326161A1 (en) 1999-10-14
NO20004921L (no) 2000-11-28
HUP0102859A2 (hu) 2001-12-28
AU746216B2 (en) 2002-04-18
KR20010042428A (ko) 2001-05-25
NO20004921D0 (no) 2000-09-29
PL343115A1 (en) 2001-07-30
EA200001016A1 (ru) 2001-02-26
DE69924990D1 (de) 2005-06-02
GB0020986D0 (en) 2000-10-11
CZ300065B6 (cs) 2009-01-21
CO4830489A1 (es) 1999-08-30
ID27055A (id) 2001-02-22
JP4258696B2 (ja) 2009-04-30
TW475340B (en) 2002-02-01
CZ20003591A3 (cs) 2001-01-17
WO1999052324A1 (en) 1999-10-14
CN1296720A (zh) 2001-05-23
BR9909901A (pt) 2000-12-26
JP2002511682A (ja) 2002-04-16
AU2947199A (en) 1999-10-25
IL138312A0 (en) 2001-10-31
GB2350008A (en) 2000-11-15
ATE294492T1 (de) 2005-05-15
BG104810A (bg) 2001-07-31
EP1068770A1 (en) 2001-01-17
GB9806994D0 (en) 1998-06-03
TR200002878T2 (tr) 2001-01-22
EA003215B1 (ru) 2003-02-27
ZA200004746B (en) 2001-06-27
AR018832A1 (es) 2001-12-12
HK1032504A1 (en) 2001-07-20
CN1143593C (zh) 2004-03-24

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