EP0965245B1 - Acoustic device - Google Patents

Acoustic device Download PDF

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Publication number
EP0965245B1
EP0965245B1 EP98907080A EP98907080A EP0965245B1 EP 0965245 B1 EP0965245 B1 EP 0965245B1 EP 98907080 A EP98907080 A EP 98907080A EP 98907080 A EP98907080 A EP 98907080A EP 0965245 B1 EP0965245 B1 EP 0965245B1
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EP
European Patent Office
Prior art keywords
acoustic
diaphragm
centre
bending
acoustic device
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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.)
Expired - Lifetime
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EP98907080A
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German (de)
English (en)
French (fr)
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EP0965245A1 (en
Inventor
Henry Azima
Martin Colloms
Neil Harris
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NVF Tech Ltd
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New Transducers Ltd
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Priority to EP01202058A priority Critical patent/EP1133212A3/en
Publication of EP0965245A1 publication Critical patent/EP0965245A1/en
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Publication of EP0965245B1 publication Critical patent/EP0965245B1/en
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    • 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
    • H04R7/10—Plane diaphragms comprising a plurality of sections or layers comprising superposed layers in contact
    • 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
    • H04R2440/00—Bending wave transducers covered by H04R, not provided for in its groups
    • H04R2440/07—Loudspeakers using bending wave resonance and pistonic motion to generate sound

Definitions

  • This invention relates to acoustic devices capable of acoustic action by bending waves and typically (but not exclusively) for use in or as loudspeakers.
  • Specific teaching includes analyses of various specific panel configurations with or without directional anisotropy of bending stiffness through/across said area(s) so as to have resonant mode vibration components distributed over said area(s) beneficially for acoustic coupling with ambient air; and as to having determinable preferential location(s) within said area(s) for acoustic transducer means, particularly operationally active or moving part(s) thereof effective in relation to acoustic vibrational activity in said area(s) and related signals, usually electrical, corresponding to acoustic content of such vibrational activity.
  • Uses are also envisaged in that PCT application for such members as or in "passive" acoustic devices, i.e.
  • transducer means such as for reverberation or for acoustic filtering or for acoustically "voicing, a space or room; and as or in "active" acoustic devices with bending wave transducer means, including in a remarkably wide range of loudspeakers as sources of sound when supplied with input signals to be converted to said sound, and also in such as microphones when exposed to sound to be converted into other signals.
  • This invention arises particularly in relation to active acoustic devices in the form of loudspeakers using panel members to perform generally as above (and as may be called distributed mode acoustic radiators/resonant panels later herein), but further particularly achieve satisfactory combination of pistonic action with bending wave action.
  • active acoustic devices in the form of loudspeakers using panel members to perform generally as above (and as may be called distributed mode acoustic radiators/resonant panels later herein), but further particularly achieve satisfactory combination of pistonic action with bending wave action.
  • more general or wider aspects of invention arise, as will become apparent.
  • WO92/03024 describes a resonant multi-modal loudspeaker comprising a radiator panel made from a skinned composite having a honeycomb core and discloses the features of the preamble of claim 1.
  • FR2,441,981 describes a diaphragm for a flat panel pistonic loudspeaker comprising a skinned composite having a honeycomb core.
  • this invention concerns active acoustic devices as defined in claim 1.
  • this invention concerns acoustic devices relying on bending wave action in panel members, particularly providing effective distributions of resonant mode vibration that may be different from what results from specific teachings and preferences of the above PCT patent application even for the same configurations or geometries.
  • this invention concerns acoustic devices relying on bending wave action in panel members, particularly providing effective distributions of resonant mode vibration in panel members of different configurations or geometries from what are regarded as inherently favourable in specific teachings and preferences of the above PCT patent application.
  • Effective inventive method and means hereof involve areal distribution of variation in stiffness over at least area(s) of such panel member(s) that are acoustically active in relation to bending wave action and desired acoustic operation.
  • variation can usefully be directly related to displacement of transducer means from a location taught in the above PCT patent application to different locations taught in this invention.
  • such variation may, relative to the above PCT application, render unfavourable configurations or geometries of panel members more akin to favourable configurations or geometries for acoustic operation involving areal distribution of resonant modes of vibration consequential to bending wave action.
  • the actual resonant mode distribution relative to above PCT application may be at least somewhat different as a result of a different areal distribution of bending stiffness or to consequential different location(s) for transducer means, or both.
  • One group/strand is as already foreshadowed, specifically providing more convenient location(s) for transducer means in acoustically active panel members or areas thereof having configurations or geometries known to be favourable in isotropic or anisotropic implementations of teachings of above PCT patent application, effectively by displacing what are now called “natural" locations for transducer means (in accordance with these patent applications), to different locations hereof, specifically by either or both of relatively greater and lesser bending stiffnesses to one side and to the other side, respectively, of such natural location(s).
  • Region(s) of greater bending stiffness serve(s) effectively to shift such natural location(s) away from such region(s), typically from said one side towards said other side and generally towards region(s) of lesser bending stiffness.
  • region(s) of lesser bending stiffness serving to shift towards region(s) of lesser bending stiffness.
  • the other group/strand can be viewed as involving capability only partially to so define at least notional sub-geometry of larger overall panel member geometry not specifically favourable to good distributed mode acoustic operation as in the above PCT patent application; such sub-geometry being incompletely circumscribed but the partial definition thereof having significant improving effect on distributed mode acoustic operation; such improving effect being particularly for distributing resonant modes therefor at lower frequencies, but not necessarily (indeed preferentially not) limiting higher frequency bending wave action and resonant mode distribution to such sub-geometry, i.e. allowing such higher frequency resonant mode distribution of vibration past and beyond the partial sub-geometry definition.
  • bending stiffness panel member(s) can have at least core layer(s) first made as substantially uniformly above PCT application, including sandwich structure(s) having skin layers over core layer(s). variation(s) of thickness can then be readily imposed to achieve desired areal distribution of stiffness(es).
  • deformable material(s) such as foam(s)
  • variation of thickness is achievable by selective compression or crushing to achieve desired contouring, say by controlled heating and application of pressure, typically to any desired profile and feasibly done even after application of any skin layers (depending on stretch capability of such skin layer material).
  • Another possibility is for the member to have localised stiffening or weakening, perhaps preferably graded series thereof.
  • Centre of mass is, of course, readily relocated, typically to geometric centre by selective addition of mass(es) to panel member(s) concerned, preferably without unacceptable effects on desired areal distribution of stiffness, e.g. masses also small enough not unacceptably to affect lower frequency bending wave action and effectively decoupled from higher frequency acoustic action(s), say small weight(s) suitably semi-compliantly mounted in hole(s) in the panel also small enough not unacceptably to affect acoustic action(s).
  • transducer location(s) hereof generally in said one direction to said one side, which can advantageously be towards geometric centre.
  • Such relative increasing/decreasing of stiffness can be complex as to resulting contouring of the panel member concerning, including tapering down increased thickness/stiffness to edge of the panel member and or sloping up decreased thickness/stiffness, say to have a substantially uniform edge thickness of the panel member.
  • an inventive aspect of at least one group/strand is seen in a panel member capable of acoustic bending wave action with a distribution of bending stiffness(es) over its acoustically active area, the distribution being in no sense centred coincidentally with centre of mass and/or geometrical centre of the panel member.
  • location(s) of acoustic transducer means may be substantially so coincident, often and beneficially so.
  • stiffness(es) over a panel member can be considered or treated as centred, one analogous to how centre of mass is usually determined, i.e. as putting first moment of stiffness to zero, thus in a sense corresponding to high stiffness (so herein called “high centre” of stiffness); the other in an inverse manner, putting first moment of the reciprocal of stiffness to zero, thus in another sense corresponding to weakness or low stiffness (so herein called “low centre” of stiffness).
  • Feasible structures of honeycomb cellular cored sandwich type can have desired stiffness distribution by reason of contributions of as-made variant individual cell geometries, and without necessarily substantial effect(s) on distribution and centre of mass.
  • desired areal distributions of stiffness(es) are achievable by variations of cells as to any or all of cell sectional area (if not also shape), cell height (effectively core thickness) and cell wall thickness, including with such degree of progressiveness applied to increase/decrease as may be desired/required.
  • Varying bending stiffness(es) without disturbing distribution of mass is achievable in such context, say by varying cell wall thickness and cell height for nominally same cell area, and/or by varying cell area and/or cell height for same thickness of cell walls, and could, of course, be augmented or otherwise affected by skin variations including varying number and/or nature of ply layers.
  • panel members hereof to have at least "low” centres of stiffness(es) and practically most effective drive location(s) that are identified and typified oppositely in terms of minimum and maximum diversity of transit times to panel edge(s) for notional or actual bending Waves considered as started from "low centre” of stiffness and from transducer location(s), respectively.
  • panel members with distribution(s) of stiffness(es) as herein can have capability applicable to securing that a said panel of some particular given or desired shape (i.e. configuration or geometry) may exhibit practically effective acoustic bending wave action that was not considered achievable hitherto for that particular shape, at least not according to any prior helpful proposition.
  • the particular shape may include unfavourable shapes which are either related to, or may be treated as related to, known favourable shapes so that what would be a characteristic of the favourable shape may be approached.
  • this invention extends to a capability of some physically realisable areal distribution of bending stiffness(es) for irregularly shaped panel members capable of bending wave acoustic action to ensure such action has a satisfactorily distributed resonant mode characteristic, and to afford practically effective location(s) for bending wave action transducer means (including by finite element analysis), irrespective of and without reference to any envisaged or target shape known to be favourable.
  • transducer location(s) including by way of notionally superposing as a target geometry a desired or given configuration of panel member and a subject geometry of a panel member that is known to be effective and for which detailed analysis is readily done or available, so that desired target transducer location coincides with actual preferentially effective transducer location of the subject geometry.
  • a bending stiffness mapping can be made so that, for any or each of selected constructs relative to now-coincident transducer locations of the target and subject geometries, and over such geometries, so that the known/readily analysed bending stiffness of the subject panel structure can be subject to transformation relative to the target geometry to give substantially the same or similar or scaled comparable stiffness distribution as in the subject geometry and acoustically successful bending wave action in the target geometry.
  • Promising such constructs include lines going from coincident transducer locations to/through edges of the target and subject geometries (say as though representing bending wave transits/traverses).
  • Envisaged related transforms depend on relative lengths of the same construct lines in the target and subject geometries, and a suitable relationship, typically involving the quotient of bending stiffness (B) and mass per unit area ( ⁇ ), i.e. B/ ⁇ , for proportionality transforms involving the third and/or fourth powers of such line lengths to edges of target and subject geometries. It is preferred, at least as feeling more natural, for a target geometry to be smaller than a related subject geometry, further preferable for superposition to seek to minimise excess of the latter over the former, including to minimise transform processing. Whilst generally similar types of target and subject shapes may thus be preferred, or favourable subject geometry closest to unfavourable target geometry, it is seen as feasible for the target geometry to differ quite substantially from any recognisable type of known favourable configuration/structure.
  • coincidence of location of bending wave transducer means with centre of mass and geometric centre is particularly effective in allowing a single transducer device at one location to combine and perform both pistonic drive and bending wave excitation.
  • a particularly interesting aspect of the invention concerning a single transducer that affords both of pistonic action and spaced bending wave action but at spaced positions, can be used whether spacing is achieved by bending wave transducer location as herein (say to suit convenient transducer configuration) or left as arises without application of above aspects of invention.
  • application of this invention may involve distributions of mass with centre of mass displaced from geometric centre and/or any transducer location, or whatever.
  • variation(s) of bending stiffness and/or mass across at least acoustically operative area(s) of panel member(s) can be in many prescribed ways and/or distributions, usually progressively in any particular direction to desired ends different from hitherto, and same will generally represent anisotropy that is asymmetric at least relative to the geometric centre of mass; and application is seen as in the above PCT application.
  • a loudspeaker drive unit comprising a chassis, a transducer supported on the chassis, a stiff lightweight panel diaphragm drivingly coupled to the transducer, and a resilient edge suspension surrounding the diaphragm and mounting the diaphragm in the chassis, wherein the transducer is arranged to drive the diaphragm pistonically at relatively low audio frequencies to produce an audio output and to vibrate the diaphragm in bending wave action at higher audio frequencies to cause the diaphragm to resonate to produce an audio output, the arrangement being such that the transducer is coupled to the centre of mass and/or geometric centre of the diaphragm and the diaphragm has a distribution of bending stiffness including variation such that acoustically effective resonant behaviour of the diaphragm results (at least preferably being centred offset from the centre of mass).
  • the diaphragm may be circular or elliptical in shape and the transducer may be coupled to the geometric centre of the diaphragm.
  • the diaphragm may comprise a lightweight cellular core sandwiched between opposed skins, and one of the skins may be extended beyond an edge of the diaphragm, with a marginal portion of the extended skin being attached to the resilient suspension.
  • the transducer may be electromagnetic and may comprise a moving coil mounted on a coil former, the coil former being drivingly connected to the diaphragm.
  • a second resilient suspension may be connected between the coil former and the chassis.
  • One end of the coil former may be connected to the diaphragm, and the said second resilient suspension may be disposed adjacent to the said one end of the coil former, and a third resilient suspension may be connected between the other end of the coil former and the chassis.
  • the end of the coil former adjacent to the panel diaphragm may be coupled to drive the panel diaphragm substantially at one point.
  • Conical means may be connected between the coil former and the panel diaphragm for this purpose.
  • the coil former may comprise a compliant section radially offset from a rigid section to drive the diaphragm pistonically and to provide off centre resonant drive to the diaphragm.
  • the invention provides a loudspeaker comprising a drive unit as described above; and/or is a stiff lightweight panel loudspeaker drive unit diaphragm adapted to be driven pistonically and to be vibrated to resonate, the diaphragm having a centre of mass located at its geometric centre and a centre of stiffness which is offset from its centre of mass.
  • a substantially rectangular acoustic distributed mode panel member 10A is indicated as though resulting directly from teachings of the above PCT and UK patent applications, thus having its "natural" location 13 for bending wave transducer means spaced from its geometrical centre 12 and off true diagonal shown dashed at 11.
  • the transducer location 13 is to be at the geometric centre 12 of the panel member 10A, i.e. effectively to appear shifted along the solid line 15, which is achieved by appropriate areal distribution of bending stiffness of the panel member.
  • the bending stiffness is made relatively greater and lesser to one side (right in Fig. 1A) and to the opposite side (left in Fig. 1C) of the geometric centre 12 and the "natural" transducer location 13, specifically in opposite directions along the line 15 and its straight-line extensions 15G and 15L, respectively.
  • Figure 1B is an outline section along the line 15 including extensions 15G and 15L, and indicates the same situation as Figure 1A, i.e. "natural" transducer location 13B likewise spaced from geometric centre 12B of distributed mode panel member 10B, see projection lines 12P, 13P.
  • Figure 1B gives no details for the actual structure of the panel member 10B; but does indicate the alternatives of being monolithic, see solid outer face lines 16X,Y, or being of sandwich type, see dashed inner face lines 17X,Y indicating skins bonded to an inner core 18, typically (though not necessarily) of cellular foam type or of honey-comb through-cell type.
  • Figure 1C indicates use of a core 18C of material that is deformable, specifically compressible in being capable of crushing to a lesser thickness, as is typically of many foamed cellular materials suitable for distributed mode acoustic panel members and assumed in Figure 1C.
  • Such crushing is indicated by thickness of the core 18C diminishing from right to left in Figure 1C, and its cells going from roundedly fully open (19X) to flattened (19Y). It is not, of course, essential for those cells to be of the same or similar size, or of regular arrangement, or be roundedly fully open at maximum thickness (suitable foam materials often being of partially compressed foamed type).
  • the core 18C is further shown with facing skins 17A,B.
  • the core material 18C it is feasible, even normal, for the core material 18C to be deformed to the desired profile before bonding-on the skins 17A,B - but not essential so long as the panel member 10C is good for distributed mode acoustic action if compressively deformed with the skins 17A,B attached. Resulting greater and lesser thickness of the core 18C and the panel member 10C will correspond with greater and lesser bending stiffness; and the indicated profile of progressive thickness, thus stiffness, variation is such as to cause coincidence of the transducer location 13C with the geometric centre 12C, see arrow 13S and circled combined reference 12C,13C. Crushing deformation will normally be done with thermal assistance and using a suitably profiled pressure plate. There will be no change to the centre of mass of the panel member 10C, i.e. centre of mass will remain coincident with the geometric centre 12C, now also coincident with the transducer location 13C.
  • the linear factor of core mass contribution may be neglected and the desired areal thickness distribution may be achieved by shaping the thickness of an isotropic core of polymer foam or fabricated honeycomb sandwich or monolithic without skin and a core; and any such structure can be fabricated, machined or moulded as desired herein.
  • Figure 1D shows distributed mode acoustic panel member 10D with progressive relief of its lower surface so that its thickness reduces with similar profile to that of Figure 1C.
  • Such profile might be somewhat different for the same intended effect, i.e. achieving coincidence of transducer location 13D with geometric centre 12D, say depending on material(s) used for the panel member 10D.
  • Such materials may be monolithic reinforced composites or any kind of cellular, typically then as a skinned core, including of honey-comb type with through-cells extending from skin-to-skin.
  • the foamed-cell-like indication 19Z of Figure 1D could correspond with use of foamed material that is by choice not crushed or is not suitable for crushing; but is intended to do no more than indicate that there is no significant change of density.
  • the panel member 10D is shown with at least one additional balancing mass 22 indicated mounted in preferably blind receiving hole 23, further preferably by semi-compliant means 24, say in a suitable mechanically or adhesively secured bush or sleeve, so that its inertial compress is progressively decoupled from the panel member 10D at higher frequencies of desired vibration distribution.
  • balancing mass 22
  • the thickness may be simply tapered along through the section of Figure 1B, though a more complex taper is normal, including to a common equal edge thickness and/or progressively less away from the line 15 - 15G, L.
  • Geometric relations of bending frequency to size need to be taken into account. For any given shape, increasing its size lowers the fundamental frequencies of vibration, and vice versa. Effective shift of preferential transducer location can be seen as equivalent to shortening the effective panel size in relation bending along the direction of such shift.
  • Figures 2A, 3A show at 26, 36 one preferentially good or best location (as in the above PCT application) for a bending wave action transducer and operative for desired resonant mode acoustic performance of the panel member 20A, 30A, say as or in a loudspeaker.
  • This different asymmetric stiffness distribution is shown achieved by progressive changes to cells 29, 39 particularly as to their heights, thus thickness of the panel members 20A, 30A; but also as to their areas and population density (see Figures 2B, C), or as to their areas and wall thicknesses but not their population density (see Figures 3B, C) thereby achieving desired distribution of stiffness without at least operatively significant disturbance to distribution of mass, thus centre of mass is now coincident with both geometric centre and transducer location (25, 26; 35, 36).
  • Figure 4A shows another application of into-surface grooving, slotting or scoring, specifically to improving distributed mode bending wave action for an acoustic panel member 40A that is actually of a configuration or geometry, namely circular, that is known to be unfavourable as a distributed mode acoustic panel member, especially with central location of exciting transducer means.
  • This known unsatisfactory performance capability is indicated by the modal frequency distribution indicated in Figure 4B as will be readily recognised and understood by those skilled in the art, specifically corresponding to concentric vibration patterning.
  • Profound improvement is shown in Figure 4C which has been achieved by grooving, slotting or scoring as indicated at 41 in the form of part of an ellipse, i.e.
  • Figures 5A, B indicate constructs and transforms much as discussed above, specifically shown for rectangular target (51A, B) and subject (52A, B) configurations/geometrie.
  • Construct lines 53A, B processed according to different lengths and desired/required bending stiffnesses show highly promising effectiveness of the approach at least as applied to shapes of the same rectangular type.
  • the methodology of Figure 5B is particularly attractive in that the subject configuration/geometry 52B is efficiently constructed from the target configuration/geometry 51B placed at one corner by extensions from that corner so that a preferential transducer location 54B of a well-understood and analysed isometric shape 52B simply coincides with geometrical centre of the target shape 51B.
  • Figure 5C indicates a typical section through target member 50 of target shape 51A resulting from methodology according to Figure 5B.
  • Figure 6A shows ratiometric results of length mapping for Figure 5B methodology
  • Figure 6B shows how required (target) bending behaviour is related to the ratiometric results of Figure 6A and relative to material properties, specifically stiffness alone involving fourth power of length (solid line), thickness of a sandwich structure involving a square power (dotted line), and thickness of a monolith structure involving a 4/3 power (dashed line).
  • skin stiffness tensile strength
  • Figure 6C shows modal density mapping with 3% damping for a target square panel member, without bending stiffness distribution hereof, a subject 1.134:1 aspect ratio isometric panel member of the above PCT application, i.e. involving adjustment relative to one side difference only; and the square panel improved by bending stiffness distribution according to skin parameters, specifically thickness (h) and Young's modulus (E).
  • a loudspeaker drive unit comprises a chassis 71 in the form of an open frame shaped as a shallow circular basket or dish having an outwardly projecting peripheral flange 71F pierced with holes whereby the drive unit can be mounted on a baffle (not shown), e.g. in a loudspeaker enclosure (not shown) in generally conventional fashion.
  • the chassis 71 supports a transducer 72 in the form of an electrodynamic drive motor comprising a magnet 73 sandwiched between pole pieces 74A,B and affording an annular gap in which is mounted a tubular coil former 75 carrying a coil 75C which forms the drive coupling or actuating movable member of the motor.
  • the coil former is mounted on resilient suspensions 76A, B at its opposite ends to guide the coil former 75 for axial movement in the gap of the magnet assembly.
  • One end of the coil former 75 is secured, e.g. by bonding 77, to the rear face of a lightweight rigid panel 70 which forms an acoustic radiator diaphragm of the loudspeaker drive unit and which comprises a lightweight cellular core 70C, e.g. of honeycomb material, sandwiched between opposed front and rear skins 70F,R.
  • the panel 70 is generally as herein taught, specifically with distribution of bending stiffness affording coincidence of centre of mass and preferential bending wave exciter location at its geometric centre.
  • the front skin is conveniently of conventional circular form integrating with the contour and in some cases blending in effective operation with the surround/suspension.
  • the rear skin is chosen to be rectangular to form a composite panel compliant with distributed mode teaching (it may be driven directly by the differential coupler of Figures 10A and 10B).
  • the distributed mode panel section will be designed with preferential modal distribution as per the invention herein generated for example by control of areal stiffness, so as usefully to place the modal driving point or region at or close to the geometric and mass centre.
  • preferential modal distribution as per the invention herein generated for example by control of areal stiffness, so as usefully to place the modal driving point or region at or close to the geometric and mass centre.
  • the front facing skin 70F of the panel 70 is extended beyond the edge of the panel and its peripheral margin is attached to a roll surround or suspension 77 supported by the chassis 71 whereby the panel is free to move pistonically.
  • the transducer 72 is arranged to move the panel 70 pistonically at low frequencies and to vibrate the panel 70 at, high frequencies to impart bending waves to the panel whereby it resonates as discussed at length above.
  • FIGS 8A and 8B are generally similar to that described above, except that in these cases the chassis 81 is even shallower, the motor 82 is largely outside the chassis 81, and the coupler/actuator coil former 85 extends into the chassis with consequent modification of its suspension 86.
  • Modification of Figure 9B involves use of a smaller neodymium motor 82N and sectional end reduction 85A of the coil former 85.
  • FIGS 10A,B show a diaphragm coupler/actuator 101, conveniently a coil former of a drive motor (not shown), having a major arcuate peripheral part 108 of its drive end, which is adapted to be attached (107) to a rigid lightweight panel 100 made of a semi-compliant material; and with arcuate peripheral part 109 of the same end rigid.
  • the drive applied to the panel 100 will be pistonic at low frequencies through both of the arcuate peripheral end parts 108,109.
  • the coupler/actuator will excite bending wave action by the minor part 109, thus vibrational energy in the panel 100 at a position offset from the axis of the coupler/actuator 105.
  • the major arcuate peripheral end part 108 will be substantially quiescent at high frequencies.
  • the true actuation position of the drive is frequency dependent even though applied in the same way and by the same means 105.
  • the simple illustrated case of one direct coupling section and one semi compliant section may be extended to multiple firm contact points and more complex semi-compliant arrangements, e.g. two or more preferential distributed mode panel member transducer locations may be involved.
  • the semi compliant section may be tapered or graded, or plurally stepped in thickness or bulk property, to provide a gradation of coupled stiffness interactively calculated with the panel acoustic performance criteria to improve overall performance, whether with a distributed mode acoustic panel with bending wave transducer location spaced from geometric/mass centre to suit convenient structure for the coupler/actuator 105, or with the latter suited to such as transducer locations of above PCT and UK patent applications.
  • Such differential frequency coupler (105) can be used with the usual motor coil employed in electrodynamic exciters. While such coupler 105 may be a separate component of predetermined size or diameter, it is convenient to see its application as part of the attachment plane of a motor coil of similar diameter, which may as indicated above be chosen to encompass one or more of the preferential drive transducer locations of a distributed mode acoustic panel member, specifically at and excited by rigid end part(s) 108 as intended higher frequency response is by bending mode vibration in a distributed mode acoustic panel diaphragm member 100.
  • the semi-resilient parts/inserts 108 become more contributory, and progressively bring the whole circumference of the actuator/coupler 105 into effect for balanced, centre of mass action, thus satisfactory pistonic operation at low frequencies.
  • the fundamental bending frequency of the panel member 100 and the resilience of the coupler/actuator part(s) 108 are chosen to allow for satisfactorily smooth transition in acoustic power from the pistonic to the bending vibration regions of the frequency range. Such transition may be further aided by plural stepping of the part(s) 108, or by tapering as indicated at 108A.
  • Fig 11B further shows displacement of effective variation of pistonic drive and distributed mode excitation points with frequency.
  • the pistonic drive point is predominantly at the centre and centre of mass. With increasing frequency there is a transition to a bending wave excitation point offset from the centre, aligned by suitable choice of panel design and also complex coupler actuator diameter and parts geometry to drive at or close to the preferred distributed mode point for satisfactory favourable distribution of vibration modes.
  • bending wave transducer means of this type with an overall diameter in the range 150 to 200mm would operate "natural" transducer location(s) of a distributed mode panel member of satisfactory bending mode performance commencing in the range 150Hz to 500Hz. Pistonic operation will be effective from lower frequencies, eg from 30Hz for a suitable acoustic mounting, and would decline in its upper range as the panel member enters the bending mode range.
  • the differential frequency capability of couplers of this invention allows subtle refinements to use of distributed mode acoustic panel members. For example, in a given panel a change in the driving point with frequency may be found desirable for purposes of frequency control seen in particular applications, such as close to wall mounting in small enclosures and related response modifying environments. More than one grade and/or size /area of semi-compliant parts or inserts may be used on suitable geometries of coupler effectively to gradually or step-wise move between more or most effective drive point of the modal pattern with frequency, and advantageously modify the radiated sound.

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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 Transducers For Audible Bands (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Transducers For Ultrasonic Waves (AREA)
  • Surgical Instruments (AREA)
  • Seal Device For Vehicle (AREA)
  • Sink And Installation For Waste Water (AREA)
  • Surface Acoustic Wave Elements And Circuit Networks Thereof (AREA)
EP98907080A 1997-03-04 1998-02-27 Acoustic device Expired - Lifetime EP0965245B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01202058A EP1133212A3 (en) 1997-03-04 1998-02-27 Acoustic device

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CN1157999C (zh) 2004-07-14
GEP20022748B (en) 2002-07-25
NZ336943A (en) 2001-02-23
AU6305398A (en) 1998-09-22
CN1249892A (zh) 2000-04-05
KR20000075889A (ko) 2000-12-26
YU39599A (sh) 2001-12-26
AU735051B2 (en) 2001-06-28
JP2001513967A (ja) 2001-09-04
IL131485A0 (en) 2001-01-28
AR011920A1 (es) 2000-09-13
NO994288L (no) 1999-09-03
EP0965245A1 (en) 1999-12-22
EE9900386A (et) 2000-04-17
HK1022398A1 (en) 2000-08-04
BR9808169A (pt) 2000-05-16
HUP0002652A3 (en) 2001-11-28
BG103669A (en) 2000-03-31
EP1133212A2 (en) 2001-09-12
PL335366A1 (en) 2000-04-25
CA2283381A1 (en) 1998-09-11
ZA981662B (en) 1998-09-03
SK119499A3 (en) 2000-08-14
GB9704486D0 (en) 1997-04-23
EA002480B1 (ru) 2002-06-27
WO1998039947A1 (en) 1998-09-11
ES2191925T3 (es) 2003-09-16
TR199902177T2 (xx) 2000-01-21
DE69810905T2 (de) 2003-12-24
HUP0002652A2 (hu) 2000-12-28
NO994288D0 (no) 1999-09-03
CZ310299A3 (cs) 1999-12-15
ID20143A (id) 1998-10-08
TW462199B (en) 2001-11-01
EP1133212A3 (en) 2006-01-11
EA199900793A1 (ru) 2000-04-24
ATE231677T1 (de) 2003-02-15
DE69810905D1 (de) 2003-02-27

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