EP1149507A2 - Generateur de sons a commande par pompe - Google Patents

Generateur de sons a commande par pompe

Info

Publication number
EP1149507A2
EP1149507A2 EP00908949A EP00908949A EP1149507A2 EP 1149507 A2 EP1149507 A2 EP 1149507A2 EP 00908949 A EP00908949 A EP 00908949A EP 00908949 A EP00908949 A EP 00908949A EP 1149507 A2 EP1149507 A2 EP 1149507A2
Authority
EP
European Patent Office
Prior art keywords
sound
pump
buffer volume
sound generator
flow
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.)
Withdrawn
Application number
EP00908949A
Other languages
German (de)
English (en)
Inventor
Oskar Bschorr
Hans-Joachim Raida
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.)
Bschorr Oskar Dr rer nat
Original Assignee
Bschorr Oskar Dr rer nat
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 Bschorr Oskar Dr rer nat, New Transducers Ltd filed Critical Bschorr Oskar Dr rer nat
Publication of EP1149507A2 publication Critical patent/EP1149507A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K15/00—Acoustics not otherwise provided for
    • G10K15/04—Sound-producing devices
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K7/00—Sirens
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R23/00—Transducers other than those covered by groups H04R9/00 - H04R21/00

Definitions

  • the invention relates to a sound generator for interference cancellation by means of anti-sound, for speech and music reproduction and for acoustic warning and information signals.
  • a compressed air flow is modulated by an electro-dynamically driven valve.
  • the modulation ratio must be as small as possible, i.e. H. that the acoustically ineffective constant air flow component is as high as possible compared to the alternating component. This worsens the acoustic efficiency in the same ratio.
  • Another loss practically by a factor of 2 results from the fact that the valve modulation not only emits useful sound into the outside, but also backward sound power into the air supply lines. This also affects the constancy of the working air pressure and thus the distortion factor deteriorates.
  • the object of the invention is a sound generator for reproducing anti-noise, speech, music and acoustic signals, which has a good, distortion-free amplitude and phase response and a high degree of efficiency with a small construction volume for the lower frequency range.
  • the conventional loudspeaker works with large diaphragm areas and small vibrations, the same delivery acceleration q ° (t) and consequently the same acoustic emission can be achieved with pumps, but with a much smaller sound-emitting opening area.
  • the dimensions of the sound-emitting opening are smaller than the sound wavelengths, so that an acoustic monopole radiator with a spherical characteristic can be realized here - without the spectral directional characteristic and phase distortion that is disturbing for loudspeakers.
  • Comparable relationships apply to a two-dimensional or generally shaped geometry.
  • (c speed of sound
  • p density in the propagation medium, e.g. air
  • r / c sound propagation time.) -
  • micro- and nanomechanical pumps contains e.g. B. the book “Fundamentals of microsystem technology” by G. Gerlach and W. Dötzel, C. Hauser Verlag, 1997.
  • the development status of the other micro- and nanomechanical components is also compiled there, especially valves, motors, oscillators, flow, pressure and temperature sensors.
  • pumps with a high delivery pressure are used to operate sound generators.
  • the pressure ratio can be further increased by connecting several pumps in series. The higher the pressure ratio, the smaller the buffer volume required to operate the monopole lamp. Compared to the boxes required for diaphragm loudspeakers, the operating volume can be considerably reduced by increasing the pressure.
  • the buffer volume and the air lines are small compared to the emitted sound wavelength and thus only have an acoustic reactance, but no resistance, so that no sound power is emitted to the rear and efficiency and reproduction are not impaired as a result.
  • reversible pumps with pressure and suction operation are used. This eliminates the reactive air flow required for the air-modulated devices with its power loss.
  • the reversal helps the over-or stored in the buffer volume. Recover vacuum energy, which again increases the efficiency and thus the operating time of mobile devices.
  • the sound-producing flow of the pumps is measured directly by means of a flow meter or indirectly by pressure and temperature sensors in the buffer volume and readjusted using a target / actual comparison.
  • the sensors required for this are also known from microsystem technology.
  • pumps and valves oscillating at the same frequency are used, the oscillation frequency of which is high compared to the useful sound frequency to be radiated.
  • the control of the flow according to size and sign is carried out by phase and / or amplitude adjustment of the pumps and valves with each other.
  • leaf springs with piezo drives or piston pumps driven by phase-controlled motors and rotary and reciprocating valves can be used.
  • the volume problem is reduced for the middle and even more for the upper frequency range. Thanks to the small volume sales, air pumps from nanotechnology are sufficient. Alternatively, conventional tweeters with crossovers are also possible.
  • the pumped air flow can also be used for electronics cooling and for air filtering and dehumidification be used.
  • an existing construction volume can be used as a buffer volume: for a watch with speech, for example, the pointer space between the dial and the watch glass; in other cases the - arbitrarily shaped - space above the control electronics.
  • Fig. 1 to 6 sound generators with buffer volumes and driven by pumping them
  • Volume flow is controllable.
  • Fig. 7 and 8 sound generators with buffer volumes and driven by constant delivery pumps and control of the volume flow through valves.
  • Fig. 9 to 12 sound generators with buffer volumes and oscillating pump delivery and with oscillating valves.
  • Fig. 13 sound generator with storage of kinetic energy in the buffer volume.
  • Fig. 14 sound generator in two-pole design. (Stereo operation)
  • Fig. 18 training the sound opening.
  • X number of the figure
  • X0 sound generator
  • XI sound opening, sound channel
  • X2, X3, X4 pump unit, pump drive, pump components
  • X5 buffer volume
  • X6, X7 modulation unit, valve, valve component
  • X8 sensors for flow, pressure and / or temperature measurement
  • X9 acoustic network, protective membrane, other components.
  • FIG. 1 shows the basic design of a sound generator 10, consisting of an air pump 12 and a buffer volume 15.
  • the air throughput - the delivery acceleration q # (t) - of the air pump 12 is controlled by an integrated pump controller 16 in accordance with the required sound signal p (t) and acts as an acoustic monopole source when exiting through the sound channel 11.
  • This idea is valid as long as the emitted sound wavelength is large compared to the diameter of the sound channel 11.
  • Line, area and volume emitters can also be synthesized in a known manner with several such “point-shaped” monopole emitters.
  • Pump systems of this type with a sufficiently high operating frequency are known from micro- and nanotechnology, which are also reversible and are suitable for both pressure and pressure
  • This has the same acoustic function as the boxes with the conventional loudspeakers.
  • the buffer volume 1 is located 5 a bore 19 with high flow resistance.
  • the pump 22 with the pump control 26 and the pump medium 24 are closed off by membranes 21 and 23.
  • the pump medium 24 can consist of air, gas or liquid.
  • a full hermetic seal is given, as z. B. is required for a speaker integrated into a clock.
  • the volume displacement of the membrane 21 acts here as a sound transmitter and is driven by the volume-controllable pump 22.
  • a buffer volume 25 again serves as compensation here; this is spherical to ensure sufficient volume rigidity even with thin walls.
  • the (pressure) pump 32 conveys air from a buffer volume 35 through the opening 31 to the outside and vice versa, the suction takes place via the opening 31 'into the buffer volume 35 through the (suction) pump 32'.
  • the net current of the openings 31 and 31 ' which is decisive for the sound radiation, can be regulated indirectly via a pressure sensor 38, which measures the pressure in the buffer volume 35.
  • two - or more - (pressure) pumps 32 and (suction) pumps 32 ' are connected in series. Doubling the pressure halves the buffer volume.
  • the pressure and suction pumps 42 and 42 ' are set to constant operating states.
  • the sound-producing, resulting flow is controlled here only by the number of pressure and suction pumps 42 and 42 'that are switched on and off. Since the time and manufacturing expenditure of micro- and nanomechanical components is practically independent of the quantity, it can be advantageous to use a large number of smaller pumps instead of just one pump. As the size becomes smaller, the reaction and start-up time of the suction and pressure pumps 42 and 42 'is reduced. In order to cover a larger dynamic range, it is advisable to use two or more pump sizes. Such a grading also does better justice to the different flow rates for low and high frequency sound radiation.
  • a Flagella pump principle This principle is used in nature in the movement of flagellates - the flagellates.
  • several waveguides 52 for mechanical transverse waves are attached in the channel of the sound opening 51.
  • the vibration exciter 54 generates in the waveguide 52 a bending or string wave with a frequency which is much higher than the sound frequency to be emitted and which propagates towards the sound opening 51.
  • the interaction of the wave with the surrounding medium, e.g. B. air or fluid exerts a force on this and thus a flow to the sound opening 51.
  • the sound-generating flow rate can thus be controlled via the power of the vibration exciter.
  • the opposite flow is controlled by the vibration exciter 54 '.
  • the interaction force that can be achieved and thus the amount of air or liquid that is of interest here is higher, the lower the speed of the flexible shaft and the lower the inherent losses of the waveguide 52.
  • Thin-walled strips and wires made of metal and fiber-reinforced plastics meet these requirements.
  • the wave has not yet fully decayed as it passes through the waveguide 52.
  • AVC active vibration control
  • the sound generator 60 consists of a buffer volume 65 of a pressure pump 62 with the blow-out opening 61 and a suction pump 62 'with the suction opening 61'. Both pumps 62 and 62 'z. B. of the Roots blower type, are driven by a motor 63 via a differential gear 64.
  • FIG. 7 and 8 are sound generators 70 and 80 which are driven by constantly delivering pumps and in which the The sound-generating air flow is controlled by valves.
  • a pump 72 sucks air from a negative pressure volume 75 ' into a positive pressure volume 75.
  • the control valve 76 releases air to the exterior to be sonicated via an opening 71.
  • air is sucked out via the valve 76 'through the opening 71 ' .
  • the delivery rate of the pump 72 depends on the sound power to be radiated and is adapted to this. In order to have a reserve in the event of a sudden increase in volume, a certain amount of reserve is expedient - in FIG.
  • FIGS. 9 to 12 have clocked pumps and valves with a clock frequency which is higher than the sound frequency to be emitted.
  • the pump piston 92 and the swing valves 96 and 97 vibrate at the same frequency.
  • the positions shown in broken lines represent the pump piston 92 and the oscillating valves 96 and 97 in the opposite amplitude position.
  • the disturbing reactive forces - all three elements 92, 96 and 97 are tuned to the same resonance frequency, but can be in their Vibration phase and amplitude can be adjusted against each other. Such an adjustment is made, for example, by the drive.
  • Piezo actuators are suitable for this in the sheet design of elements 92, 96 and 97 used in FIG.
  • the acoustically effective flow at the opening 91 can be adjusted according to direction and size.
  • the delivery flow which is dependent on the sound power to be emitted, is set via the oscillation amplitudes of the pump piston 92.
  • pump pistons 92 and the valves 96 and 97 in rotary design can be built and driven by phase-controllable motors.
  • a buffer volume 95 is provided in order to have monopoly radiation again. This can be dispensed with if the sound openings 91 and 91 'act on two acoustically separated rooms.
  • the buffer volume 105 of a sound generator 100 is designed as a ⁇ / 2 resonator.
  • a standing wave is generated by the oscillating piston 102.
  • the natural resonance of the oscillation valve 106 is matched to the ⁇ / 2 resonance.
  • the phase position and the amplitudes of the oscillating piston 102 and oscillating valve 106 allow the volume flow at the opening 101 to be controlled again according to direction and amount.
  • a valve disk 116 driven by the motor 117 with a rotational frequency equal to the frequency of the ⁇ / 2 vibration has openings and is closed on the radially opposite side thereof.
  • air is conveyed to the outside; if the phase is under vacuum, suction takes place.
  • the middle position there is no resulting air flow from the openings 111 and 111 '.
  • the exemplary embodiment according to FIG. 12 is the two-dimensional analog to the one-dimensional embodiment according to FIG. 10.
  • the sound-producing air flow of the openings 121 and 121 ' can be controlled by their phase position.
  • the buffer volume 135 in FIG. 13 stores not only pressure but also kinetic energy.
  • the air in the buffer volume 135 is set in rotation by an essentially constantly rotating rotor 132.
  • a valve flap 136 is attached to the circumference of the buffer volume. In position 136 ', air is conveyed to the outside and in the opposite position 136' ', the rotational movement sucks in air from the outside according to the principle of the gas jet pump. This principle can be expanded by connecting a second, idle buffer volume.
  • Fig. 14 shows a two-pole sound generator 140, e.g. is useful for stereo playback or when realizing an acoustic dipole.
  • two independent pump drives 142 and 142 'with the associated loudspeaker openings 141 and Hl' are provided.
  • Each unit can be designed according to one of the exemplary embodiments in FIGS. 1 to 12.
  • a common buffer volume 145 is provided here; in extreme cases this can degenerate into a connecting tube.
  • a common buffer volume for all individual poles can also be advantageous. The same applies to an array arrangement for directional sound radiation. Standing waves in the buffer volume 145 are dampened by sound absorbers 149.
  • 15 to 17 are means to switch off the clock and other intrinsic noises of the pumps and the valves.
  • destructive interference cancellation is carried out by bringing together two openings 151 and 151 'of pumps and valves which are shifted by 180 ° in time. Such an arrangement transforms a monopole emitter into a less effective dipole. A quad arrangement with a quadrupole property results in a further reduction of the clock noise. The useful sound is not affected.
  • the opening channel 161 is filled with sound-absorbing fiber materials 169. The noise from the high-frequency pumps and valves is damped much more than the low-frequency useful noise. At the same time, dust filtering can be carried out with the fibers 169.
  • the loudspeaker channel 171 is designed with — here — Helmholtz resonators 179. This allows the clock frequency and its harmonics to be absorbed or damped in a targeted manner without disturbing the useful sound. As a result, the acoustically usable volume flow of the loudspeaker channel 171 is also smoothed.
  • the sound channel 181 has a cross-sectional expansion.
  • This extension is designed as an aerodynamic diffuser and is used for large flow rates, i.e. at high flow velocities to ensure reversible pressure compensation without lossy vortex formation.
  • - not shown here channel subdivisions, an adjacent, vortex-free flow can be maintained even with short channel lengths.
  • the design of the sound channel 181 as a diffuser does not meet the requirements of an acoustic horn. Of course, a horn can be installed downstream.
  • the sound channel 181 is provided with a protective grille 189 against contamination and interference.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Signal Processing (AREA)
  • Electrostatic, Electromagnetic, Magneto- Strictive, And Variable-Resistance Transducers (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Obtaining Desirable Characteristics In Audible-Bandwidth Transducers (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un générateur de sons pour la suppression d'interférences au moyen d'une absorption de bruit et pour la reproduction de signaux acoustiques, de signaux vocaux et de musique. La production de sons s'effectue de préférence par l'intermédiaire de pompes à air micromécaniques et nanomécaniques (12), dont le débit est régulé par l'organe de commande (16) en fonction du signal sonore requis, l'air sortant de la pompe par un canal acoustique (11); le canal complémentaire (11') agit sur un volume tampon fermé (15). Comme dans une enceinte acoustique classique, ce volume tampon (15) a pour fonction de créer un émetteur acoustique monopolaire à partir du dipôle inefficace du canal acoustique (11) et du canal (11'). Dans le cas des pompes à air (12), présentant des rapports de compression élevés, le volume tampon nécessaire est faible. Au moyen d'un débitmètre micromécanique (18), le débit volumétrique générateur de sons est mesuré dans le canal acoustique (11) et peut être réajusté après une comparaison valeur prescrite/valeur réelle. Un orifice (19) présentant une résistance élevée à l'écoulement provoque dans le volume tampon une compensation des variations de pression d'air et des erreurs de dérive.
EP00908949A 1999-02-02 2000-01-28 Generateur de sons a commande par pompe Withdrawn EP1149507A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19904106A DE19904106C2 (de) 1999-02-02 1999-02-02 Schallgenerator mit Pumpantrieb
DE19904106 1999-02-02
PCT/DE2000/000252 WO2000047012A2 (fr) 1999-02-02 2000-01-28 Generateur de sons a commande par pompe

Publications (1)

Publication Number Publication Date
EP1149507A2 true EP1149507A2 (fr) 2001-10-31

Family

ID=7896152

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00908949A Withdrawn EP1149507A2 (fr) 1999-02-02 2000-01-28 Generateur de sons a commande par pompe

Country Status (7)

Country Link
EP (1) EP1149507A2 (fr)
JP (1) JP2003501849A (fr)
KR (1) KR20020007299A (fr)
CN (1) CN1339237A (fr)
AU (1) AU3144300A (fr)
DE (1) DE19904106C2 (fr)
WO (1) WO2000047012A2 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10309517B4 (de) * 2003-03-05 2006-04-13 Reissig, Sergej, Dr.-Ing. Lautsprecherbox
DE20303510U1 (de) 2003-03-05 2003-06-12 Reissig, Sergej, Dr.-Ing., 91058 Erlangen Lautsprecherbox
US8855329B2 (en) 2007-01-22 2014-10-07 Silentium Ltd. Quiet fan incorporating active noise control (ANC)
KR100932204B1 (ko) * 2007-10-25 2009-12-16 한국기계연구원 자가전원 기능을 갖는 ｍｅｍｓ 구조 인공와우의 주파수분석기
JP6182524B2 (ja) 2011-05-11 2017-08-16 シレンティウム リミテッド ノイズ・コントロールのデバイス、システム、および方法
US9928824B2 (en) 2011-05-11 2018-03-27 Silentium Ltd. Apparatus, system and method of controlling noise within a noise-controlled volume
DE102012217844A1 (de) * 2012-07-06 2014-01-09 Siemens Medical Instruments Pte. Ltd. Pumpeinrichtung für Hörgerät
EP3036735A1 (fr) * 2013-08-21 2016-06-29 Board of Regents, The University of Texas System Dispositifs acoustiques non réciproques fondés sur une sollicitation à quantité de mouvement linéaire ou angulaire
US10354638B2 (en) * 2016-03-01 2019-07-16 Guardian Glass, LLC Acoustic wall assembly having active noise-disruptive properties, and/or method of making and/or using the same
US10134379B2 (en) 2016-03-01 2018-11-20 Guardian Glass, LLC Acoustic wall assembly having double-wall configuration and passive noise-disruptive properties, and/or method of making and/or using the same
US10304473B2 (en) 2017-03-15 2019-05-28 Guardian Glass, LLC Speech privacy system and/or associated method
US10726855B2 (en) 2017-03-15 2020-07-28 Guardian Glass, Llc. Speech privacy system and/or associated method
US10373626B2 (en) 2017-03-15 2019-08-06 Guardian Glass, LLC Speech privacy system and/or associated method
US11931776B2 (en) 2018-12-26 2024-03-19 Industrial Technology Research Institute Actuator, method for manufacturing the actuator, and acoustic transmitter
CN111365621B (zh) * 2018-12-26 2022-01-11 财团法人工业技术研究院 致动器及其制法与音波发射器
CN111678544B (zh) * 2020-06-05 2023-09-15 南京俏声波动科技有限公司 一种平衡双向输出高压波源装置及其工作方法
DE102022209000A1 (de) 2022-08-30 2024-02-29 Sivantos Pte. Ltd. Hörgerät

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3618106A1 (de) * 1986-05-30 1987-12-03 Siemens Ag Piezoelektrisch betriebene fluidpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL9201278A (nl) * 1992-03-10 1993-10-01 Jacobus Lambertus Van Merkstei Systeem voor het onderdrukken van geluid.
US5257914A (en) * 1992-06-24 1993-11-02 Warren Rupp, Inc. Electronic control interface for fluid powered diaphragm pump
DE19539020C2 (de) * 1995-10-19 1999-04-22 Siemens Ag Pumpe zur Förderung gasförmiger oder flüssiger Medien

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3618106A1 (de) * 1986-05-30 1987-12-03 Siemens Ag Piezoelektrisch betriebene fluidpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO0047012A3 *

Also Published As

Publication number Publication date
WO2000047012A2 (fr) 2000-08-10
WO2000047012A3 (fr) 2000-12-21
AU3144300A (en) 2000-08-25
DE19904106A1 (de) 2000-08-03
DE19904106C2 (de) 2001-06-28
JP2003501849A (ja) 2003-01-14
KR20020007299A (ko) 2002-01-26
CN1339237A (zh) 2002-03-06

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