EP1110426B1 - Dispositif acoustique en forme de panneau utilisant des modes a ondes de flexion - Google Patents

Dispositif acoustique en forme de panneau utilisant des modes a ondes de flexion Download PDF

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Publication number
EP1110426B1
EP1110426B1 EP99941742A EP99941742A EP1110426B1 EP 1110426 B1 EP1110426 B1 EP 1110426B1 EP 99941742 A EP99941742 A EP 99941742A EP 99941742 A EP99941742 A EP 99941742A EP 1110426 B1 EP1110426 B1 EP 1110426B1
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EP
European Patent Office
Prior art keywords
panel
bending stiffness
bending
stiffness
exciter
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EP99941742A
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German (de)
English (en)
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EP1110426A1 (fr
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Henry Azima
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NVF Tech Ltd
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New Transducers Ltd
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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
    • 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

Definitions

  • the invention relates to panel form acoustic apparatus using bending wave modes and in particular to loudspeakers incorporating such panels.
  • a transducer is coupled to a stiff panel capable of bending wave oscillations.
  • the bending wave oscillations are distributed over the required frequency range, and couple to the air.
  • the technology is often used in loudspeakers, in which case the transducer is an exciter that excites bending wave oscillations in the panel resulting in an acoustic output.
  • a distributed mode acoustic device that can also be operated pistonically.
  • the distribution of bending stiffness is arranged such that the centre of bending stiffness is offset from the exciter position
  • the coil mass may have a stronger influence as its impedance becomes comparable to the panel impedance at a lower frequency, affecting high frequency roll-off.
  • the aperture resonance of the panel material inside the voice coil which occurs when the panel wavelength is comparable to the exciter diameter, takes place at a lower frequency for a less stiff panel. This effect can be evident as a peak in the sound pressure.
  • the low frequency performance of a large panel of lower stiffness is relatively poor.
  • a panel-form acoustic member capable of supporting bending wave vibration, wherein the bending stiffness and/or areal mass density in the panel varies over the area of the panel to produce a range of coincidence frequencies having a ratio of maximum to minimum coincidence frequency of at least 1.2 to 1 so that bending waves in the panel are coupled to the air more uniformly with respect to acoustic power and/or directivity as compared to an isotropic panel.
  • a range of coincidence of 1.2 to 1 produces in embodiments a moderate effect. However, a larger range of at least 1.5 to 1 or preferably at least 2 to 1 may allow a greater effect.
  • coincidence is not a subject of theory or textbook teaching. Although the coincidence effect is known it is treated as a difficulty to be avoided. Alternative methods teach adding mass to the member or coupled layer damping and are generally isotropic treatments.
  • the panel form acoustic member may be incorporated in any of a number of possible acoustic devices. Accordingly, there may be provided an acoustic absorber, an acoustic resonator for reverberation control, an acoustic enclosure, or a support for audio components including such a panel form acoustic member.
  • a microphone having a panel-form acoustic member as described above and a transducer for converting bending waves in the member into electrical signals.
  • a loudspeaker comprising a panel member capable of supporting bending waves in the audio frequency range, an exciter on the panel member for exciting bending waves in the panel to produce an acoustic output, wherein the bending stiffness of the panel member varies with position over the area of the panel member, so that the effect of coincidence on the acoustic output of the panel is smoothed.
  • the effects of coincidence on the acoustic output include beaming of sound above the coincidence frequency or discontinuities or peaks in the sound output pressure or power as a function in frequency, integrated over the whole forward hemisphere and/or in particular directions. Using the invention, any or all of these effects may be reduced.
  • a variation of bending stiffness causes an additional change in the velocity of sound in the panel and hence a variation of the coincidence frequency.
  • the direction of acoustic radiation may accordingly vary over the surface of the panel.
  • the variation of bending stiffness may thus be arranged to cause the distribution of the radiated sound to be spread over a larger angle, to reduce beaming.
  • the power output as a function of frequency often has a peak, step or discontinuity at the coincidence frequency. This irregularity may be smoothed by varying the coincidence frequency.
  • the coincidence frequency is inversely related to the bending stiffness, and may normally be varied by varying the bending stiffness. This in turn can be achieved by varying the thickness of the panel.
  • the panel may be stiffer at the exciter location since the aperture resonance caused by a coupling of the coil mass over a finite area is at an advantageously higher frequency for a stiffer panel.
  • the bending stiffness may have a maximum near the exciter position.
  • the panel can be made symmetric with a maximum in its centre so that the preferred off-centre exciter position for distributed mode panels is close to, but not at, the minimum of coincidence frequency, normally the maximum of bending stiffness.
  • close to is meant sufficiently close that the bending stiffness at the exciter is at least 70% of its maximum; preferably 80% and further preferably 90% higher.
  • the panel may be stiffer at the edges of the panel than the centre.
  • the coincidence frequency is still smoothed by the variation in stiffness.
  • the exciter may be located on the thin region of the panel, where the mechanical impedance of the panel is less. This can aid coupling of lower frequency energy into the panel.
  • the panel may have a maximum bending stiffness within the central region (the central third both across and along the panel) and reduce in stiffness towards the edges.
  • Such a panel may be formed by injection moulding by gating from the thicker central region of the panel.
  • the invention may provide the benefits of a large stiff panel whilst reducing some of the disadvantages, in particular the effects of a coincidence frequency within the audio range.
  • the bending stiffness has to vary over a region of the panel of linear dimension comparable or greater thanthe wavelength of sound in the frequency range of interest. This may typically be 3 to 4cm for a frequency of 10kHz. A very small area of increased bending stiffness is accordingly not suitable to smooth the effects of coincidence. Variation over an area of linear size at least 1.5 times, preferably double the wavelength at coincidence is thus suitable. A variation over an area of at least 5% of the panel area, preferably 10%, may be beneficial for reducing coincidence effects.
  • the bending stiffness variation may be concentrated at the exciter position.
  • the gradient of bending stiffness may be high close to the exciter position and slowly reduce along lines extending outwards from the exciter position.
  • such a profile gives a useful smoothing of coincidence effects.
  • the gradient can reduce to zero at the edge of the exciter region or the variation can extend to the edge of the panel.
  • the bending stiffness may be constant in the region of the panel far away from the exciter, with all of the variation of bending stiffness concentrated in the exciter region.
  • the bending stiffness may also be varied in a strip around the edge of the panel member.
  • the bending stiffness may be maximum at the edge and reduce towards a level in the interior of the panel, or may be a minimum at the edge and increase.
  • Such a panel may have its edge clamped in a frame: the variation of bending stiffness at the edge can then create a desired match or mismatch between the mechanical impedance of the panel and that of the clamping for further control of acoustic output.
  • the bending stiffness may in particular vary in the edge strip that is no more than a distance of 10% of the length of the panel from the edge.
  • a reduction in stiffness close to the panel edge reduces the mechanical impedance of the panel in the edge region. If this reduced impedance is less than that of a clamping frame little energy is transferred from the panel to the frame.
  • an increase in peripheral stiffness will increase the mechanical impedance of the panel in that region. If the panel is supported on a resilient support then the increase in panel impedance may create a larger mismatch to minimise unwanted energy transfer to the frame. Conversely, if the panel is connected to a rigid clamp type frame, then this can provide a smoother transition from the panel to the clamped edge and so aid the mechanical robustness of the final construction.
  • a rapidly varying bending stiffness near the edge may reflect acoustic vibration energy back into the interior of the panel so little energy reaches the frame.
  • the bending stiffness may vary rapidly in the edge region and be relatively constant in the interior of the panel. Alternatively, the bending stiffness may vary over both the edge region and the interior. The bending stiffness may also vary both in the region of the exciter and around the edge, with a region of little or no stiffness variation between the edge and the exciter regions.
  • Another option is to vary the bending stiffness in an undulating pattern over the panel, or in a plurality of steps.
  • any parameter may be varied that changes the velocity in the panel and accordingly the coincidence frequency. Accordingly, it is possible to vary the Young's modulus of the skin, or the areal density of the skin or core.
  • Figure 1 shows a loudspeaker comprising a panel (1) with an exciter (3) attached thereto.
  • the exciter (3) excites resonant bending waves in the panel to cause the panel to emit sound.
  • Electrical conductors (5) connect the exciter to an amplifier.
  • the panel (1) is in this embodiment made from a core (7) and two skins (9). Alternatively, the panel may be monolithic.
  • the panel used in the loudspeaker can be a distributed mode panel, as described in WO97/09842 and other applications, where a useful frequency response is achieved by distributing the resonant modes evenly in frequency, and it advantageous if the modes are distributed over the panel.
  • the shape of the panel and exciter location can be selected.
  • Some specific suitable shapes are taught in WO97/09842, for example a rectangle of aspect ratio 1:0.882 or 1:0.707, for an isotropic panel. Some adjustment to these ratios may be required depending on the panel thickness profile.
  • the exciter locations are also important.
  • the exciter position should couple to the distributed resonant modes. Some good exciter positions are located near but not at the centre of the panel. For an isotropic rectangular panel, one such position is at coordinates referred to the lengths of the sides of (3/7,4/9), close to the panel centre coordinates at (1/2,1/2).
  • the preferred coordinates will vary from these values, which may however still make suitable starting points to find optimal locations by trial and error.
  • laser or computational analysis will help identify effective exciter positions.
  • a cost-effective ways of manufacturing a bending wave panel is by injection moulding. This is not only of moderate unit cost and capable of producing consistent results, but also certain features of attachment of the panel to both exciters and panel support frame, and fixing arrangements may also be included in the mouldings as an integral part of the panel, saving on parts and assembly costs. Injection moulding is effective with panels that are thicker in the middle and taper towards the edge, as forseen.
  • coincidence frequency the parameter considered useful to control in a distributed mode speaker
  • f c the coincidence frequency
  • the sound radiation is more strongly emitted at a wide angle which angle reduces towards the normal axis as frequency is increased.
  • the change of radiation angle, from below the coincidence frequency to above, causes a spatial energy shift, which can be undesirable.
  • aperture effects limit the high frequency performance of less stiff panels. Clamped distributed mode loudspeakers makes possible the use of less stiff panels, but, adding to the mass density may be generally undesirable as it will cause loss in efficiency.
  • the wavelength of the bending waves in the frequency region around coincidence changes over the panel. For example, in a case where the thickness increases from the centre outwards, the wave velocity increases to the panel edges. Conversely, the wave velocity would reduce when the taper is reversed. This changes the eigenvectors associated with bending waves over the panel surface area.
  • the panel stiffness gradient may be changed in a variety of ways. Suitable methods include:
  • Injection moulding processes are eminently suitable for making bending wave panels in quantity, at low cost and in a consistent manner. Whilst monolithic radiators can be moulded in a straightforward fashion, they may not be suitable in some applications.
  • a preferred method suitable for moulding is to create a thickness change outwards with positive or negative gradient. By controlling the foaming agent in the core of the panel a large stiffness gradient may be created across the panel. In a monolithic panel, stiffness changes with the cube power of thickness, while in a sandwich type panel it changes approximately with the square of thickness.
  • stiffness gradient when the stiffness gradient is positive in directions towards the panel edges, stiffness may be increased by design to create a smooth transition to a clamped edge panel design. This can give added mechanical robustness of the final construction.
  • Excitation of the panel may be achieved in any desired manner e.g. as described in our various prior patent applications.
  • the objective remains to excite the panel modes evenly and with a view to achieving a good degree of smoothness in the mechanical impedance (for input of mechanical power), and/or the acoustic radiated power within the design bandwidth.
  • Such optimised position(s) may be obtained by analysis, e.g. FE methods or empirically.
  • Acoustic power is the integration of the sound pressure level over all angles.
  • a characteristic which is a smooth function of frequency is often a factor in sound quality.
  • the irregularity in the power output of bending wave panels at coincidence may be spread in frequency by tapering the panel thickness. Increasing the stiffness away from the drive point should spread coincidence to lower frequency; conversely, decreasing the stiffness spreads the range to higher frequencies.
  • the increased radiation coupling strength above coincidence means that more of the energy input into the panel is radiated close to the excitation position. Further away from the exciter, the panel velocity is progressively reduced and little power is radiated. Consequently variation in panel thickness should be concentrated relatively close to the exciter or the variation will occur in part of the panel that does not radiate strongly and will have little effect. This has the further advantage that the variation in panel thickness will cause less alteration of performance at lower frequencies: at lower frequencies (below coincidence) the radiation efficiency is much reduced and the energy will be in the form of resonant bending wave modes distributed in frequency and over the whole panel surface.
  • the coupling to radiation is lower and the in addition the sound is radiated over a larger area relative to the panel.
  • the panel variation in stiffness / wave velocity should therefore be concentrated over a larger area.
  • the area over which the variation should be apportioned will also depend on the structural material damping, if this is larger than the radiation damping.
  • the required profile to spread the coincidence effect will depend on panel mass density, bending stiffness, shear properties, and damping properties.
  • the variation of bending stiffness of the panel should also widen the directivity.
  • the sound radiation will be spread to a larger angle to the normal to the panel.
  • the sound radiation will be spread to a smaller angle to the normal to the panel. Either way, the range of angles is increased.
  • the directivity of the radiation from the panel is much harder to smooth than the acoustic power, as the following discussion illustrates.
  • the different parts of the panel with different bending wave velocities, radiate in different directions resulting in a particular polar plot of sound energy as a function of direction.
  • the panel velocity increases and the angle of radiated sound decreases towards the axis position, according to the above formula.
  • the differential of angle with respect to velocity is large for large angles, and decreases as the angle decreases towards the on-axis position. Therefore as the frequency is increased, the sound is emitted in a pattern which changes shape. The energy is focussed into a narrower beam around the normal axis.
  • the polar plot changes shape with increasing frequency. By specifically varying the bending stiffness over the panel a more uniform sound output can be achieved for a given frequency but the summation of outputs may produce a less smooth output at other frequencies.
  • the sound pressure level at one listening angle can be arranged to remain relatively constant. However, elsewhere the sound pressure may no longer be constant and may show increased beaming effects.
  • the drive point chosen was at the centre of the panel in order to simplify the profile of the test panels.
  • the exciter was a 4 ohm NEC electrodynamic exciter with a 13mm diameter voice coil.
  • Figure 3a shows the bending wave velocity calculated from the material parameters of the panel, for three different uniform thicknesses of panel: 4mm, 3mm and 2mm respectively.
  • Figure 3b shows the experimental determination of the panel velocity for these panels, found from the image of the vibration pattern in the panel at fixed frequencies. At low frequencies the predicted values agree with the experimental results. However, at high frequencies the measured velocity is less than the predicted value due to the influence of shear. The velocity varies more slowly with frequency than the square root dependence expected for pure bending at high frequencies.
  • a line labelled "c" representing the speed of sound in air.
  • the frequencies at which this line crosses the velocity trace for each panel thickness is the coincidence frequency.
  • the prediction/calculation from the static or low frequency bending stiffness suggests an increase in the coincidence frequency from approximately 5kHz to 8.5 kHz when the panel thickness is reduced from 4mm to 2mm. In practice this change in thickness results in a much greater variation in coincidence frequency from 5kHz to 14kHz.
  • the 4mm panel had a 5kHz coincidence frequency, the 3mm a 7kHz coincidence frequency and the 2mm panel a 14kHz coincidence frequency.
  • the tapered panels described later have a thickness of 4mm at the drive point, reducing to 2mm at the edge.
  • Figure 4 shows measurements of the single point frequency response on axis and at 40° and 80° off axis. As the angle is increased away from the on-axis position the low frequencies are attenuated due to some acoustic cancellation. At 80° a high frequency peak occurs at close to 5kHz, the coincidence frequency of this panel. The peak sound output at 80° reaches 80dB which is approximately 14 dB greater than the on-axis response at this frequency. This peak in the response followed by a degree of attenuation is characteristic of the coincidence effect in a large stiff panel.
  • Figure 5 shows the polar plots of the sound pressure level in different directions at 6kHz, 9kHz and 15kHz.
  • the narrowing of the radiation is clear, starting at 90° for 6kHz decreasing to less than 60° at 15kHz. This beaming to radiate at an angle that decreases with increasing frequency is characteristic of the coincidence effect.
  • Figure 6 shows the acoustic power as a function of frequency. At low frequencies the power is slowly varying. However as the frequency is further increased the power rises to a maximum close to the coincidence frequency then falls back at higher frequency. The maxiumum is much broader than that seen in the sound pressure level traces in Figure 5. This is because the power measurement is an integration of the sound pressure level over all angles and therefore does not reflect the changing directivity, only the total acoustic output which varies relatively slowly with frequency. This maximum in the power response is also characteristic of the coincidence effect as seen in large stiff bending radiators.
  • the loudspeaker has a tapered panel.
  • Figure 7a shows the profile of the tapered panel as a function of the fractional distance to the edge of the panel.
  • the panel was milled to this profile in both the x and y planes, forming a pyramid shape in the central region.
  • Figure 7b Also shown in Figure 7b is the corresponding graph of the coincidence frequency, which shows that the greater variation is located relatively close to the exciter position.
  • Figure 8 shows the single point frequency responses for increasing angle around the panel.
  • the on-axis response is similar to the reference panel in both high and low frequency extension.
  • the coincidence maximum shown by the flat panel is attentuated by up to 10dB in this embodiment.
  • the width of the maximum is also increased, by a factor of approximately 2.
  • Figure 9 shows the polar plots of the sound pressure level at the same frequencies of 6kHz, 9kHz and 15kHz shown in Figure 5. It is clear from a comparison of these two figures that the polar plot of the panel according to the first embodiment shows significantly less beaming than the reference flat panel.
  • Figure 10 shows the acoustic power radiated by the panel according to the first embodiment.
  • the coincidence maximum is attenuated by 5dB and is broadened to higher frequency, as predicted for a tapered panel with a decreasing stiffness towards the edge.
  • the tested panel shows a significant improvement over the flat panel in all aspects of the problems due to coincidence. As such it represents a good compromise of the panel profile with significant improvements in each aspect of the problems of coincidence whilst retaining a good frequency response.
  • Both panels represent a good compromise that improves all aspects of the coincidence radiation characteristics.
  • the second panel shows a slightly degraded set of single point frequency responses and acoustic power traces relative to the first, whereas the single frequency polar plot results are slightly improved. While the optimisation will always be a compromise, the designer may choose according to the requirements of the application.
  • the first two embodiments relate to a panel of moderate size.
  • a third embodiment will now be discussed of small size, (A5 - 210 by 148.5mm).
  • Figures 15 and 16 show the panel profile. As can be seen, it is very highly tapered.
  • the panel is made from 14.5mm thick Rohacell compressed to 10.8mm at the centre and 1mm at the edge.
  • the control flat panel is compressed to 9.8mm over its whole surface.
  • the exciter is mounted on the rear of the panel at a position that is optimal for a isotropic panel. Good results are obtained with this exciter position even for the tapered panel, though a further optimisation of exciter position would be envisaged.
  • Figure 16 shows a plot of coincidence frequency calculated as a function of position over the panel. Comparative results of a 10mm flat panel of the same size and the tapered panel are shown in Figure 17. Acoustic power measurements are shown in Figure 18a (flat panel) and Figure 18b (tapered panel).
  • the panel demonstrates excellent wide directivity: even at 13kHz sound is radiated evenly into the front hemisphere.
  • the power response of the tapered panel also does not show a significant step around 5kHz; such a step is clearly visible in the reference panel response.
  • these test panels are mounted on a shallow box, which gives rise to the maximum around 500Hz. This would need to be controlled in a practical loudspeaker, by an electrical filter or otherwise. It is caused by the box, not the taper.
  • Figures 19 to 21 show measurements of the drive point velocity of three panels, excited by a transducer with a voice coil diameter of 25mm.
  • Figure 19 shows the results of a 4mm flat panel
  • Figure 20 the results from the panel of the first embodiment
  • Figure 21 the results from a 2mm flat panel.
  • Aperture resonance is evident in the velocity traces as a sharp peak between 10kHz and 20kHz.
  • the resonance occurs at 13.1kHz.
  • the resonance occurs at 11.8kHz.
  • the resonance frequency for the flat panels increases with increasing panel stiffness.
  • the resonance frequency for the tapered panel is determined by the panel thickness at the drive point, and is therefore similar to the 4mm thick flat panel.
  • the panel In order to make a practical speaker the panel is often mounted in some frame/support.
  • the aim here is to keep the vibrational energy in the panel, with minimum transmission to the frame. This is achieved with a large impedance mismatch between the panel and frame. Varying the panel thickness at the edge allows the impedance at the panel/frame boundary to be controlled without significantly affecting the overall radiation characteristics. A few examples where such an approach might be beneficial will now be presented.
  • a sharp increase/decrease in panel thickness at the boundary should reflect energy back into the body of the panel.
  • sharply increasing the panel thickness at the edge provides an approximation to a clamped boundary and the energy incident on the boundary is reflected back into the panel. The edge can then be safely clamped or supported as it contains very little vibrational energy.
  • Figure 22 shows a panel which is of constant thickness but in which the radius of curvature varies over the panel area. This causes a variation in bending stiffness.
  • Figure 23 An alternative approach is illustrated in Figure 23. A panel is corrugated as shown, to achieve a higher bending stiffness in the central region than in the outer region.
  • the thickness of the panel also does not need to vary in the simple ways shown above.
  • the bending stiffness can vary over the surface in an undulating pattern, or in a series of steps over the surface of the panel.
  • a few possible profiles are shown in Figure 24. Such profiles can be achieved by corresponding undulations and steps in the thickness of the panel, or otherwise.

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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)
  • Building Environments (AREA)

Claims (25)

  1. Un élément acoustique sous la forme d'un panneau (1) capable de supporter une vibration d'ondes de flexion, dans lequel la rigidité en flexion et/ou la masse surfacique dans le panneau varient sur l'étendue du panneau (1) pour procurer une plage de fréquences de coïncidence ayant un rapport entre la fréquence de coïncidence maximale et la fréquence de coïncidence minimale d'au moins 1,2 à 1, de façon que des ondes de flexion dans le panneau (1) soient couplées à l'air plus uniformément en ce qui concerne la puissance acoustique et/ou la directivité, en comparaison avec un panneau isotrope.
  2. Un dispositif acoustique comprenant un élément acoustique sous la forme d'un panneau (1) selon la revendication 1 et un transducteur couplé à l'élément.
  3. Un haut-parleur comprenant un élément acoustique sous la forme d'un panneau (1) selon la revendication 1 et un excitateur (3) couplé au panneau (1) pour exciter des ondes de flexion dans l'élément de façon à produire une émission acoustique, dans lequel l'effet de coïncidence sur l'émission acoustique du panneau est lissé.
  4. Un haut-parleur selon la revendication 3, dans lequel la rigidité en flexion du panneau (1) varie sur une aire d'au moins 10% de l'aire du panneau.
  5. Un haut-parleur selon la revendication 3 ou 4, dans lequel la rigidité en flexion a une valeur maximale et l'excitateur (3) est couplé au panneau (1) à une position ayant une rigidité en flexion au moins égale à 70% de la valeur maximale.
  6. Un haut-parleur selon l'une quelconque des revendications 3 à 5, dans lequel l'épaisseur du panneau varie sur l'étendue du panneau (1) de façon à procurer une plage de rigidité en flexion et donc de fréquences de coïncidence.
  7. Un haut-parleur selon l'une quelconque des revendications 3 à 6, dans lequel la rigidité en flexion a un maximum dans la région centrale du panneau (1) et diminue vers les bords.
  8. Un haut-parleur la revendication 7, dans lequel l'excitateur (3) est couplé au panneau (1) près du maximum de rigidité en flexion.
  9. Un haut-parleur selon l'une quelconque des revendications 3 à 8, dans lequel l'excitateur (3) est positionné à un maximum de rigidité en flexion du panneau (1).
  10. Un haut-parleur selon l'une quelconque des revendications 3 à 7. dans lequel la rigidité du panneau a un minimum au centre du panneau (1) et augmente vers les bords du panneau (1).
  11. Un haut-parleur selon la revendication 10, dans lequel l'excitateur (3) est placé près du centre du panneau (1) dans une région de rigidité inférieure à la rigidité moyenne du panneau (1).
  12. Un haut-parleur selon la revendication 10 ou 11, dans lequel l'un au moins des bords du panneau (1) est bloqué, et la rigidité en flexion du panneau (1) est maximale à au moins un bord bloqué.
  13. Un haut-parleur selon l'une quelconque des revendications 3 à 12, dans lequel le gradient de rigidité en flexion est concentré près de la position de l'excitateur.
  14. Un haut-parleur selon la revendication 13, dans lequel le gradient de rigidité en flexion est élevé à proximité de la position de l'excitateur (3) et diminue lentement le long de lignes s'étendant vers l'extérieur à partir de la position de l'excitateur.
  15. Un haut-parleur selon l'une quelconque des revendications 2 à 14, dans lequel la rigidité en flexion varie autour du bord de l'élément consistant en un panneau.
  16. Un haut-parleur selon la revendication 15, dans lequel la rigidité en flexion est la plus élevée aux bords du panneau (1) et diminue progressivement vers l'intérieur du panneau (1).
  17. Un haut-parleur selon la revendication 15 ou 16, dans lequel au moins un bord est bloqué sur un support.
  18. Un haut-parleur selon la revendication 17, dans lequel la rigidité en flexion au bord du panneau (1) est telle que l'impédance mécanique du panneau (1) à son bord soit désadaptée vis-à-vis de celle du support (13).
  19. Un haut-payeur selon l'une quelconque des revendications 3 à 6, dans lequel la rigidité en flexion du panneau (1) varie en une configuration ondulée, de façon à lisser l'effet de coïncidence sur l'émission acoustique.
  20. Un haut-parleur selon l'une quelconque des revendications 3 à 19, dans lequel le panneau (1) est un panneau à modes répartis ayant une multiplicité de modes d'ondes de flexion résonnants répartis en fréquence.
  21. Un absorbant acoustique comprenant un élément acoustique sous la forme d'un panneau (1) conforme à la revendication 1.
  22. Un résonateur acoustique pour la maítrise de la réverbération, comprenant un élément acoustique sous la forme d'un panneau (1) conforme à la revendication 1.
  23. Une enceinte acoustique incluant un élément acoustique sous la forme d'un panneau (1) conforme à la revendication 1.
  24. Un support pour des composants audio, dans lequel le support comprend un élément acoustique sous la forme d'un panneau (1) conforme à la revendication 1.
  25. Un dispositif acoustique selon la revendication 2, dans lequel le transducteur convertit des ondes de flexion dans le panneau (1) en un signal électrique, de façon que le dispositif acoustique fonctionne comme un microphone.
EP99941742A 1998-09-02 1999-09-01 Dispositif acoustique en forme de panneau utilisant des modes a ondes de flexion Expired - Lifetime EP1110426B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9818959 1998-09-02
GBGB9818959.0A GB9818959D0 (en) 1998-09-02 1998-09-02 Panelform loudspeaker
PCT/GB1999/002724 WO2000015000A1 (fr) 1998-09-02 1999-09-01 Dispositif acoustique en forme de panneau utilisant des modes a ondes de flexion

Publications (2)

Publication Number Publication Date
EP1110426A1 EP1110426A1 (fr) 2001-06-27
EP1110426B1 true EP1110426B1 (fr) 2004-02-25

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EP99941742A Expired - Lifetime EP1110426B1 (fr) 1998-09-02 1999-09-01 Dispositif acoustique en forme de panneau utilisant des modes a ondes de flexion

Country Status (27)

Country Link
EP (1) EP1110426B1 (fr)
JP (1) JP2002524994A (fr)
KR (1) KR20010074943A (fr)
CN (1) CN1157998C (fr)
AR (1) AR020361A1 (fr)
AT (1) ATE260534T1 (fr)
AU (1) AU5524299A (fr)
BG (1) BG105261A (fr)
BR (1) BR9913391A (fr)
CA (1) CA2342764A1 (fr)
DE (1) DE69915083T2 (fr)
EA (1) EA002629B1 (fr)
GB (1) GB9818959D0 (fr)
HK (1) HK1034407A1 (fr)
HU (1) HUP0103191A2 (fr)
ID (1) ID28655A (fr)
IL (1) IL141634A0 (fr)
NO (1) NO20011080L (fr)
PE (1) PE20001147A1 (fr)
PL (1) PL346418A1 (fr)
SK (1) SK2842001A3 (fr)
TR (1) TR200100682T2 (fr)
TW (1) TW465252B (fr)
UY (1) UY25689A1 (fr)
WO (1) WO2000015000A1 (fr)
YU (1) YU17201A (fr)
ZA (1) ZA200100759B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014012327B3 (de) * 2014-08-20 2015-12-03 Helge Bots Resonanzplatte zur Verbesserung der Klangcharakteristik herkömmlicher Lautsprecherboxen
EP3101911B1 (fr) * 2015-06-04 2023-06-21 Amina Technologies Limited Oscillations d'amortissement de haut-parleur en mode distribué à l'intérieur de pieds d'excitation
WO2023247017A1 (fr) * 2022-06-21 2023-12-28 Huawei Technologies Co., Ltd. Système vibratoire comprenant un panneau vibratoire avec une structure de trou noir acoustique

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002060218A1 (fr) * 2001-01-26 2002-08-01 Harman Audio Electronic Systems Gmbh Haut-parleur a membrane
GB0007025D0 (en) * 2000-03-23 2000-05-10 New Transducers Ltd Loudspeakers
DE10025460B4 (de) * 2000-05-23 2004-03-18 Harman Audio Electronic Systems Gmbh Hochtonlautsprecher
US7120263B2 (en) 2001-03-23 2006-10-10 New Transducers Limited Bending wave acoustic radiator
US7062051B2 (en) 2001-08-17 2006-06-13 New Transducers Limited Acoustic device
SE523321C2 (sv) * 2002-06-20 2004-04-13 Covial Device Ab Sätt och anordning för avkänning och indikering av akustisk emission
JP2005236352A (ja) * 2004-02-17 2005-09-02 Authentic Ltd 表示装置用パネル型スピーカ
CA2560659A1 (fr) 2004-04-16 2005-10-27 New Transducers Limited Dispositif acoustique et procede de fabrication de celui-ci
DE102004028664A1 (de) * 2004-06-12 2006-01-19 Puren Gmbh Schwingungskörper eines Lautsprechersystems
GB0414082D0 (en) * 2004-06-24 2004-07-28 New Transducers Ltd Bending wave devices
DE102004061314A1 (de) * 2004-12-20 2006-07-06 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Lautsprechermemebran und Verfahren zum Herstellen einer Lautsprechermembran
ITMI20051106A1 (it) * 2005-06-13 2006-12-14 Enrico Ciresa S R L Pannello sonoro per la diffusione di suoni e musica e relativo procedimento di fabbricazione.
JP4779526B2 (ja) * 2005-09-15 2011-09-28 日本電気株式会社 パネルスピーカ
EP1952667A1 (fr) 2005-11-14 2008-08-06 Nxp B.V. Systeme de deplacement asymetrique pour un haut-parleur piezoelectrique et haut-parleur asymetrique
GB0601076D0 (en) * 2006-01-19 2006-03-01 New Transducers Ltd Acoustic device and method of making acoustic device
JP5541022B2 (ja) * 2010-09-10 2014-07-09 株式会社村田製作所 振動装置
JP2012119882A (ja) * 2010-11-30 2012-06-21 Murata Mfg Co Ltd 振動装置
DE102013010654A1 (de) 2013-06-26 2014-12-31 Tobias Weiss Biegewellenlautsprecher
DE102015217778B4 (de) * 2015-09-17 2019-05-29 Robert Bosch Gmbh Akustischer Sensor mit einer Membran und einem elektroakustischen Wandler
GB2551723B (en) * 2016-06-27 2018-11-28 Amina Tech Limited Speaker Panel
GB2564061B (en) * 2016-06-27 2020-12-16 Amina Tech Limited Speaker panel
US10264348B1 (en) * 2017-12-29 2019-04-16 Nvf Tech Ltd Multi-resonant coupled system for flat panel actuation
DE102018106333A1 (de) * 2018-03-19 2019-09-19 HELLA GmbH & Co. KGaA Sensorvorrichtung zur Erfassung von Schall, insbesondere zur Erfassung von Körperschall an einem Fahrzeug
GB2586959B (en) * 2019-08-08 2021-10-13 Amina Tech Limited Distributed mode loudspeaker
CN112584288B (zh) * 2020-12-09 2023-03-14 青岛海信激光显示股份有限公司 发声板及投影屏幕
WO2022121590A1 (fr) * 2020-12-09 2022-06-16 青岛海信激光显示股份有限公司 Panneau de génération sonore et écran de projection
KR20230004191A (ko) * 2021-06-30 2023-01-06 엘지디스플레이 주식회사 음향 장치와 이를 포함하는 음향 시스템

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3247925A (en) * 1962-03-08 1966-04-26 Lord Corp Loudspeaker
DE69106712T2 (de) * 1990-08-04 1995-06-08 Secr Defence Brit Paneelförmiger lautsprecher.
US5425107A (en) * 1992-04-09 1995-06-13 Bertagni Electronic Sound Transducers, International Corporation Planar-type loudspeaker with dual density diaphragm
UA51671C2 (uk) * 1995-09-02 2002-12-16 Нью Транзд'Юсез Лімітед Акустичний пристрій
GB9704486D0 (en) * 1997-03-04 1997-04-23 New Transducers Ltd Acoustic devices etc

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014012327B3 (de) * 2014-08-20 2015-12-03 Helge Bots Resonanzplatte zur Verbesserung der Klangcharakteristik herkömmlicher Lautsprecherboxen
EP2988524A1 (fr) 2014-08-20 2016-02-24 Helge Bots Panneau de resonance pour perfectionner le fidélité du son d' haut-parleurs conventionnel
EP3101911B1 (fr) * 2015-06-04 2023-06-21 Amina Technologies Limited Oscillations d'amortissement de haut-parleur en mode distribué à l'intérieur de pieds d'excitation
WO2023247017A1 (fr) * 2022-06-21 2023-12-28 Huawei Technologies Co., Ltd. Système vibratoire comprenant un panneau vibratoire avec une structure de trou noir acoustique

Also Published As

Publication number Publication date
EP1110426A1 (fr) 2001-06-27
CA2342764A1 (fr) 2000-03-16
PL346418A1 (en) 2002-02-11
TR200100682T2 (tr) 2001-10-22
JP2002524994A (ja) 2002-08-06
BR9913391A (pt) 2001-05-22
ATE260534T1 (de) 2004-03-15
EA200100303A1 (ru) 2001-08-27
NO20011080D0 (no) 2001-03-02
CN1317220A (zh) 2001-10-10
CN1157998C (zh) 2004-07-14
ZA200100759B (en) 2001-08-27
HUP0103191A2 (hu) 2001-12-28
GB9818959D0 (en) 1998-10-21
IL141634A0 (en) 2002-03-10
AU5524299A (en) 2000-03-27
DE69915083T2 (de) 2004-10-14
KR20010074943A (ko) 2001-08-09
NO20011080L (no) 2001-05-02
DE69915083D1 (de) 2004-04-01
TW465252B (en) 2001-11-21
ID28655A (id) 2001-06-21
WO2000015000A1 (fr) 2000-03-16
EA002629B1 (ru) 2002-08-29
HK1034407A1 (en) 2001-10-19
UY25689A1 (es) 1999-11-17
BG105261A (bg) 2001-08-31
PE20001147A1 (es) 2000-11-06
AR020361A1 (es) 2002-05-08
YU17201A (sh) 2003-07-07
SK2842001A3 (en) 2001-09-11

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