EP0897468A1 - Air intake system for an internal combustion engine - Google Patents

Air intake system for an internal combustion engine

Info

Publication number
EP0897468A1
EP0897468A1 EP97923023A EP97923023A EP0897468A1 EP 0897468 A1 EP0897468 A1 EP 0897468A1 EP 97923023 A EP97923023 A EP 97923023A EP 97923023 A EP97923023 A EP 97923023A EP 0897468 A1 EP0897468 A1 EP 0897468A1
Authority
EP
European Patent Office
Prior art keywords
volume
damping volume
combustion engine
internal combustion
damping
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.)
Granted
Application number
EP97923023A
Other languages
German (de)
French (fr)
Other versions
EP0897468B1 (en
Inventor
Rolf Füsser
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.)
Mann and Hummel GmbH
Original Assignee
Filterwerk Mann and Hummel GmbH
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 Filterwerk Mann and Hummel GmbH filed Critical Filterwerk Mann and Hummel GmbH
Publication of EP0897468A1 publication Critical patent/EP0897468A1/en
Application granted granted Critical
Publication of EP0897468B1 publication Critical patent/EP0897468B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/14—Combined air cleaners and silencers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1205—Flow throttling or guiding
    • F02M35/1222—Flow throttling or guiding by using adjustable or movable elements, e.g. valves, membranes, bellows, expanding or shrinking elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1205—Flow throttling or guiding
    • F02M35/1227—Flow throttling or guiding by using multiple air intake flow paths, e.g. bypass, honeycomb or pipes opening into an expansion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1261—Helmholtz resonators

Definitions

  • the invention relates to an intake device for an internal combustion engine according to the preamble of the main claim.
  • an intake device which provides an additional volume on the intake device for noise damping which is not flowed through by the intake air.
  • a suction device for a combustion engine is also known from DE-OS 40 41 786, in which a controllable shut-off device is provided to vary the passage opening through which the sucked-in air flows.
  • the shut-off device is located in a transverse channel located between two suction channels and is opened or closed by control commands from control electronics. The control commands are dependent on the speed of the internal combustion engine and on the temperature of the outside air, which is determined with a temperature sensor.
  • a disadvantage of the prior art is that a not inconsiderable part of the intake or damper volume is switched off or is not effective for the intake. This is disadvantageous given the scarcity of available space in the engine compartment of modern motor vehicles.
  • the invention is based on the object of developing an intake device for an internal combustion engine according to the preamble of the main claim so that optimum operating conditions, in particular noise conditions, are present for all operating states of the internal combustion engine and in the available space in the engine compartment.
  • the suction device according to the invention achieves the stated object with the features specified in the characterizing part of the main claim.
  • the suction device according to the invention is advantageous in that the volume of the suction device as a whole is always effective, but the noise-reducing effect can be varied in such a way that the optimal damping several speed ranges with different effects can be distributed.
  • the intake pipe in the damper volume can be opened in a simple manner. Due to the sound propagation in the volume, a Helmholtz resonator defined by the volume size is effective, which promotes the propagation of a certain sound frequency range and dampens another range.
  • a branch pipe interference pipe
  • the damping volume can be connected to the air filter volume over a large area, so that this direct coupling results in an addition of the damping volume to the air filter volume, which also has a damping effect.
  • the so-called Helmholtz resonance is determined by this volume sum and is correspondingly low-frequency, which leads to noise damping in the lower speed range of the internal combustion engine.
  • the embodiment according to claim 4 describes the flexible switching possibility of the desired sizes and the physical properties of the damping volume. Due to its adaptability, this switching technology brings about good acoustic properties of the internal combustion engine or the motor vehicle. The required switching effort can be achieved in a simple manner using the other units of a motor vehicle according to claim 5. Expensive and expensive additional devices outside the suction device are not required according to the invention. drawing
  • Figure 1 is a schematic representation of a suction device with a switchable damper volume in a first
  • Figure 2 is a schematic diagram of a suction device with a switchable damper volume in a second
  • Figure 3 is a schematic representation of a suction device with a switchable damper volume in a third
  • FIG. 1 shows a suction device 1 for an internal combustion engine, not shown here, through which an air flow according to arrow 2 is sucked through an air filter 3.
  • an intake pipe 4 leads through a damping volume 5 to a throttle valve actuator 6 and ultimately to the intake pipe 7 of the internal combustion engine.
  • An additional channel 8 is arranged between the air filter 3 and the damping volume 5.
  • a flap 10 for closing the additional duct 8
  • a pipe switch 11 for opening the suction pipe 4 inside the damping volume 5
  • a branch pipe 12 which extends from the suction pipe 4 a predetermined length parallel to the suction pipe 4 , however opposite to the air flow 2, runs and is open at the end.
  • the damping volume is connected to the air filter 3 over a large area, since the flap 10 is open to the additional duct 8.
  • the Helmholtz resonance mentioned above is therefore determined by the sum of all open volumes and is accordingly low-frequency.
  • FIG. 4 in which the size of the sound emission (dB (A)) as a function of the speed (rpm) is shown in all operating modes.
  • a curve 21 according to FIG. 4 shows an example of the relatively large damping in the lower speed range.
  • FIG. 2 shows a switch position in which both the flap 10 for the additional duct and the pipe switch 11 are closed.
  • the damping volume 5 acts as a Helmholtz resonator in the bypass, since only the branch pipe 12 can be considered as the coupling element of the intake pipe 4 to the damping volume 5.
  • Such shunt resonators are suitable for selectively steaming specific noise components or sound frequencies by means of a suitable length of the branch pipe 12. This sound position according to FIG. 2 is therefore suitable for use in the entire speed range.
  • FIG. 4 shows a curve 20 of the sound emission over the rotational speed when the branch pipe 12 is dimensioned with a shunt resonance of 40 Hz, for damping very low sound frequencies.
  • FIG. 3 is a switch position for a two-chamber volume in which the damping volume 5 and the volume of the air filter 3 are connected in series.
  • the two are Chambers each coupled via a damper neck.
  • This is a series connection of two separate Helmholtz resonators, which leads to attenuation, in particular of the high sound frequencies.
  • the course of the sound emission in this switching position is shown in FIG. 4 as curve 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Exhaust Silencers (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

The invention concern an air intake system for an internal combustion engine. The intaken air passes via an air filter (3) to the internal combustion engine. Within the intake passage an attenuation volume (5) is provided which acts as a Helmholtz resonator. The size of the attenuating volume is such that a given noise frequency range can be attenuated. To achieve optimum noise reduction at least a partial flow of air passes through the attenuation volume (5) and the size of the effective attenuation volume (5) through which the air passes can be varied by reversible switches and valves.

Description

Ansauαvorrichtunα für einen Verbrennungsmotor Ansauαvorrichtunα for an internal combustion engine
Die Erfindung betrifft eine Ansaugvorrichtung für einen Verbrennungsmotor nach dem Oberbegriff des Hauptanspruchs .The invention relates to an intake device for an internal combustion engine according to the preamble of the main claim.
Stand der TechnikState of the art
Bei Verbrennungsmotoren für Kraftfahrzeuge werden zur Er¬ zielung eines optimalen Betriebsverhaltens Ansaugsysteme bevorzugt, die kein starres Ansaugvolumen aufweisen sondern eine Anpassung an unterschiedliche Anforderungen des Motor¬ betriebs gestatten. Auch die Geräuschdämpfung spielt hier eine große Rolle.In internal combustion engines for motor vehicles, intake systems which do not have a rigid intake volume but rather allow adaptation to different requirements of engine operation are preferred in order to achieve optimum operating behavior. Noise reduction also plays a major role here.
Aus der EP 0 569 714 AI ist eine Ansaugvorrichtung bekannt, die zur Geräuschdämpfung ein Zusatzvolumen an der Ansaug¬ vorrichtung vorsieht, das nicht von der Ansaugluft durch¬ strömt wird. Es sind hier zwei wahlweise zuschaltbare Reso¬ nanzrohre (Interferenzrohre) vorhanden, die bei bestimmten Drehzahlen des Verbrennungsmotors eine Dämpfung der stören¬ den Schallfrequenzen vornehmen.From EP 0 569 714 A1 an intake device is known which provides an additional volume on the intake device for noise damping which is not flowed through by the intake air. There are two optionally switchable resonance tubes (interference tubes) which dampen the disturbing sound frequencies at certain engine speeds.
Es ist weiterhin eine Ansaugvorrichtung für einen Verbren¬ nungsmotor aus der DE-OS 40 41 786 bekannt, bei der zur Variierung der Durchtrittsöffnung, durch die die angesaugte Luft strömt, ein steuerbares Absperrorgan vorhanden ist. Das Absperrorgan befindet sich in einem zwischen zwei An¬ saugkanälen befindlichen Querkanal und wird durch Steuerbe¬ fehle einer Steuerelektronik geöffnet oder geschlossen. Die Steuerbefehle sind abhängig von der Drehzahl des Verbren¬ nungsmotors und von der Temperatur der Außenluft, die mit einem Temperaturfühler ermittelt wird.A suction device for a combustion engine is also known from DE-OS 40 41 786, in which a controllable shut-off device is provided to vary the passage opening through which the sucked-in air flows. The shut-off device is located in a transverse channel located between two suction channels and is opened or closed by control commands from control electronics. The control commands are dependent on the speed of the internal combustion engine and on the temperature of the outside air, which is determined with a temperature sensor.
Nachteilig ist beim Stand der Technik, daß ein nicht unbe¬ trächtlicher Teil des Ansaug- bzw. Dämpfervolumens abge¬ schaltet wird oder für die Ansaugung nicht wirksam ist . Bei der Knappheit des zur Verfügung stehenden Platzes im Motor¬ raum moderner Kraftfahrzeuge ist dies unvorteilhaft.A disadvantage of the prior art is that a not inconsiderable part of the intake or damper volume is switched off or is not effective for the intake. This is disadvantageous given the scarcity of available space in the engine compartment of modern motor vehicles.
AufgabenstellungTask
Der Erfindung liegt die Aufgabe zugrunde, eine Ansaugvor¬ richtung für einen Verbrennungsmotor nach dem Oberbegriff des Hauptanspruchs so fortzubilden, daß für alle Betriebs- zustände des Verbrennungsmotors und bei dem zur Verfügung stehenden Platz im Motorraum optimale Betriebs- insbesonde¬ re Geräuschverhältnisse vorliegen.The invention is based on the object of developing an intake device for an internal combustion engine according to the preamble of the main claim so that optimum operating conditions, in particular noise conditions, are present for all operating states of the internal combustion engine and in the available space in the engine compartment.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Ansaugvorrichtung löst die gestellte Aufgabe mit den im Kennzeichen des Hauptanspruchs angegebe¬ nen Merkmalen.The suction device according to the invention achieves the stated object with the features specified in the characterizing part of the main claim.
Vorteilhaft ist die erfindungsgemäße Ansaugvorrichtung da¬ durch, daß das Volumen der Ansaugvorrichtung insgesamt im¬ mer wirksam ist, die geräuschmindernde Wirkung jedoch der¬ art variiert werden kann, daß die optimale Dämpfung auf mehrere Drehzahlbereiche mit unterschiedlicher Wirkung ver¬ teilt werden kann.The suction device according to the invention is advantageous in that the volume of the suction device as a whole is always effective, but the noise-reducing effect can be varied in such a way that the optimal damping several speed ranges with different effects can be distributed.
Mit einer Rohrweiche gemäß Anspruch 2 kann das Ansaugrohr im Dämpfervolumen auf einfache Weise geöffnet werden. Durch die Schallausbreitung in dem Volumen wird ein durch die Vo¬ lumengröße definierter Helmholtz-Resonator wirksam, der die Ausbreitung eines bestimmten Schallfrequenzbereichs fördert und einen andern Bereich dämpft. Durch eine Parallelschal¬ tung eines Abzweigrohres (Interferenzrohr) gemäß Anspruch 2 können aufgrund von Interferenzen bestimmte Schallfrequen¬ zen, abhängig von der Länge des Abzweigrohres, selektiv be¬ dämpft werden.With a pipe switch according to claim 2, the intake pipe in the damper volume can be opened in a simple manner. Due to the sound propagation in the volume, a Helmholtz resonator defined by the volume size is effective, which promotes the propagation of a certain sound frequency range and dampens another range. Through a parallel connection of a branch pipe (interference pipe) according to claim 2, certain sound frequencies can be damped selectively depending on the length of the branch pipe due to interference.
Mit der Anordnung eines Zusatzkanals nach Anspruch 3 kann das Dämpfungsvolumen großflächig an das Luftfiltervolumen angeschlossen werden, so daß sich durch diese direkte Kopplung eine Addition des Dämpfungsvolumens mit dem eben¬ falls dämpfend wirkenden Luftfiltervolumen ergibt. Die so¬ genannte Helmholtzresonanz wird durch diese Volumensumme bestimmt und ist entsprechend niederfrequent, was zu einer Geräuschdämpfung im unteren Drehzahlbereich des Verbren¬ nungsmotors führt .With the arrangement of an additional channel according to claim 3, the damping volume can be connected to the air filter volume over a large area, so that this direct coupling results in an addition of the damping volume to the air filter volume, which also has a damping effect. The so-called Helmholtz resonance is determined by this volume sum and is correspondingly low-frequency, which leads to noise damping in the lower speed range of the internal combustion engine.
Die Ausführungsform gemäß Anspruch 4 beschreibt die flexi¬ ble Umschaltmöglichkeit der gewünschten Größen und der phy¬ sikalischen Eigenschaften des Dämpfungsvolumens. Diese Um¬ schalttechnik bewirkt durch seine Anpassungsfähigkeit gute akustische Eigenschaften des Verbrennungsmotors bzw. des Kraftfahrzeugs. Der erforderliche Schaltaufwand ist unter Ausnutzung der sonstigen Aggregate eines Kraftfahrzeuges nach Anspruch 5 auf einfache Weise zu realisieren. Aufwen¬ dige und teure Zusatzeinrichtungen außerhalb der Ansaugvor¬ richtung sind gemäß der Erfindung nicht erforderlich. ZeichnungThe embodiment according to claim 4 describes the flexible switching possibility of the desired sizes and the physical properties of the damping volume. Due to its adaptability, this switching technology brings about good acoustic properties of the internal combustion engine or the motor vehicle. The required switching effort can be achieved in a simple manner using the other units of a motor vehicle according to claim 5. Expensive and expensive additional devices outside the suction device are not required according to the invention. drawing
Ein Ausführungsbeispiel der erfindungsgemäßen Ansaugvor¬ richtung wird anhand der Zeichnung erläutert. Es zeigen:An embodiment of the intake device according to the invention is explained with reference to the drawing. Show it:
Figur 1 eine Prinzipdarstellung einer Ansaugvorrichtung mit einem umschaltbaren Dämpfervolumen in einer erstenFigure 1 is a schematic representation of a suction device with a switchable damper volume in a first
SchaltStellung;Switching position;
Figur 2 eine Prinzipdarstellung einer Ansaugvorrichtung mit einem umschaltbaren Dämpfervolumen in einer zweitenFigure 2 is a schematic diagram of a suction device with a switchable damper volume in a second
SchaltStellung;Switching position;
Figur 3 eine Prinzipdarstellung einer Ansaugvorrichtung mit einem umschaltbaren Dämpfervolumen in einer drittenFigure 3 is a schematic representation of a suction device with a switchable damper volume in a third
Schaltstellung undSwitch position and
Figur 4 Kurvenverläufe der Schallemission in den obigenFigure 4 curves of the sound emission in the above
Schaltstellungen in Abhängigkeit von der Drehzahl desSwitch positions depending on the speed of the
Verbrennungsmotors.Internal combustion engine.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist eine Ansaugvorrichtung 1 für einen hier nicht dargestellten Verbrennungsmotor gezeigt, durch die ein Luftstrom gemäß Pfeil 2 durch einen Luftfilter 3 ange¬ saugt wird. Nach dem Luftfilter 3 führt ein Ansaugrohr 4 durch ein Dämpfungsvolumen 5 zu einem Drosselklappensteller 6 und letztendlich zum Saugrohr 7 des Verbrennungsmotors. Zwischen dem Luftfilter 3 und dem Dämpfungsvolumen 5 ist ein Zusatzkanal 8 angeordnet.FIG. 1 shows a suction device 1 for an internal combustion engine, not shown here, through which an air flow according to arrow 2 is sucked through an air filter 3. After the air filter 3, an intake pipe 4 leads through a damping volume 5 to a throttle valve actuator 6 and ultimately to the intake pipe 7 of the internal combustion engine. An additional channel 8 is arranged between the air filter 3 and the damping volume 5.
Im Inneren des Dämpfungsvolumens 5 befindet sich eine Klap¬ pe 10 zum Verschließen des Zusatzkanals 8, eine Rohrweiche 11 zum Öffnen des Ansaugrohres 4 in daε Innere des Dämp¬ fungsvolumens 5 und ein Abzweigrohr 12, das vom Ansaugrohr 4 eine vorgegebene Länge parallel zum Ansaugrohr 4, jedoch entgegengesetzt zum Luftstrom 2, verläuft und am Ende offen ist.In the interior of the damping volume 5 there is a flap 10 for closing the additional duct 8, a pipe switch 11 for opening the suction pipe 4 inside the damping volume 5 and a branch pipe 12 which extends from the suction pipe 4 a predetermined length parallel to the suction pipe 4 , however opposite to the air flow 2, runs and is open at the end.
In der Darstellung nach Figur 1 ist das Dämpfungsvolumen großflächig an den Luftfilter 3 angeschlossen, da die Klap¬ pe 10 zum Zusatzkanal 8 geöffnet ist. Die oben erwähnte Helmholtzresonanz ist daher von der Summe aller geöffneter Volumina bestimmt und entsprechend niederfrequent . Zur Ver¬ deutlichung dieses Sachverhalts wird auf Figur 4 verwiesen, in der die Größe der Schallemission (dB(A)) in Abhängigkeit von der Drehzahl (U/min) in allen Betriebsarten aufgezeigt ist. Eine Kurve 21 nach Figur 4 zeigt beispielhaft die ver¬ hältnismäßig große Dämpfung im unteren Drehzahlbereich.In the illustration according to FIG. 1, the damping volume is connected to the air filter 3 over a large area, since the flap 10 is open to the additional duct 8. The Helmholtz resonance mentioned above is therefore determined by the sum of all open volumes and is accordingly low-frequency. To clarify this fact, reference is made to FIG. 4, in which the size of the sound emission (dB (A)) as a function of the speed (rpm) is shown in all operating modes. A curve 21 according to FIG. 4 shows an example of the relatively large damping in the lower speed range.
In Figur 2 ist eine Schaltstellung dargestellt, bei der so¬ wohl die Klappe 10 zum Zusatzkanal als auch die Rohrweiche 11 geschlossen sind. Hier wirkt das Dämpfungsvolumen 5 als Helmholtz-Resonator im Nebenschluß, da als Kopplungselement des Ansaugrohres 4 zum Dämpfungsvolumen 5 nur das Abzwei¬ grohr 12 in Betracht kommt. Solche Nebenschlußresonatoren sind dazu geeignet, durch eine geeignete Länge des Abzwei¬ grohres 12, gezielt bestimmte Geräuschanteile bzw. Schall- frequenzen selektiv zu bedampfen. Damit ist diese Schallt- Stellung nach Figur 2 dazu geeignet im gesamten Drehzahlbe¬ reich eingesetzt zu werden. In der Figur 4 ist ein Verlauf 20 der Schallemission über der Drehzahl bei einer Bemessung des Abzweigrohres 12 bei einer Nebenschlußresonanz von 40Hz, zur Bedämpfung sehr tiefer Schallfrequenzen darge¬ stellt.FIG. 2 shows a switch position in which both the flap 10 for the additional duct and the pipe switch 11 are closed. Here, the damping volume 5 acts as a Helmholtz resonator in the bypass, since only the branch pipe 12 can be considered as the coupling element of the intake pipe 4 to the damping volume 5. Such shunt resonators are suitable for selectively steaming specific noise components or sound frequencies by means of a suitable length of the branch pipe 12. This sound position according to FIG. 2 is therefore suitable for use in the entire speed range. FIG. 4 shows a curve 20 of the sound emission over the rotational speed when the branch pipe 12 is dimensioned with a shunt resonance of 40 Hz, for damping very low sound frequencies.
Bei der Darstellung nach Figur 3 handelt es sich um eine Schaltstellung für ein Zwei-Kammer-Volumen bei der das Dämpfungsvolumen 5 und das Volumen des Luftfilters 3 hin¬ tereinander geschaltet sind. Durch das Öffnen der Rohrwei¬ che 11 und das Schließen des Zusatzkanals 8 sind die beiden Kammern jeweils über einen Dämpferhals miteinander gekop¬ pelt. Es handelt sich hierbei um eine Hintereinanderschal¬ tung von zwei separaten Helmholtz-Resonatoren, die zu einer Bedämpfung insbesondere der hohen Schallfrequenzen führt. Der Verlauf der Schallemission bei dieser Schaltstellung ist in der Figur 4 als Kurve 22 gezeigt.3 is a switch position for a two-chamber volume in which the damping volume 5 and the volume of the air filter 3 are connected in series. By opening the pipe switch 11 and closing the additional duct 8, the two are Chambers each coupled via a damper neck. This is a series connection of two separate Helmholtz resonators, which leads to attenuation, in particular of the high sound frequencies. The course of the sound emission in this switching position is shown in FIG. 4 as curve 22.
Aus der Figur 4 ist insgesamt ersichtlich, daß bei einer geeigneten Verknüpfung der drei beschriebenen Schaltstel¬ lungen ein optimierter Verlauf der Schallemission über der Drehzahl des Verbrennungsmotors erreichbar ist . Es kann so¬ mit für jeden Drehzahlbereich ein geeignetes wirksames Vo¬ lumen für einen Helmholtz-Resonator zur adaptiven Geräu¬ schminderung bei Verbrennungsmotoren eingesetzt werden. Overall, it can be seen from FIG. 4 that with a suitable combination of the three switching positions described, an optimized course of the sound emission can be achieved over the speed of the internal combustion engine. A suitable effective volume for a Helmholtz resonator for adaptive noise reduction in internal combustion engines can thus be used for each speed range.

Claims

PatentansprücheClaims
1) Ansaugvorrichtung für einen Verbrennungsmotor1) Intake device for an internal combustion engine
- bei dem die angesaugte Luft über einen Luftfilter (3) zum Verbrennungsmotor geführt ist und im Bereich des Ansaugwegs ein als Helmholtz-Resonator wirkendes Dämpfungsvolumen (5) angeordnet ist, wobei die Größe des resultierenden Volumens derart bemessen ist, daß ein vorgegebener Schallfrequenzbe¬ reich dämpfbar ist, dadurch gekennzeichnet, daß- In which the intake air is guided to the internal combustion engine via an air filter (3) and a damping volume (5) acting as a Helmholtz resonator is arranged in the area of the intake path, the size of the resulting volume being dimensioned such that a predetermined sound frequency range is dampable, characterized in that
- das Dämpfungsvolumen (5) von der angesaugten Luft zumin¬ dest teilweise durchströmt ist und daß- The damping volume (5) is at least partially flowed through by the intake air and that
- die Größe des durchströmten Dämpfungsvolumens (5) vari¬ ierbar ist .- The size of the damping volume (5) through which flow is variable.
2) Ansaugvorrichtung nach Anspruch 1, dadurch geken¬ nzeichnet, daß2) Suction device according to claim 1, characterized geken¬ that
- das Ansaugrohr (4) durch das Dämpfungsvolumen (5) geführt ist und innerhalb des Dämpfungsvolumens (5) mittels einer Rohrweiche (11) zum Dämpfungsvolumen (5) hin offenbar und wieder verschließbar ist und daß - am Ansaugrohr (4) im Dämpfungsvolumen (5) ein offenes Ab¬ zweigrohr (12) mit vorgegebener Länge in das Dämpfungsvolu¬ men (5) entgegengesetzt zur Richtung (2) des Luftstroms parallel zurückgeführt ist.- The suction pipe (4) is guided through the damping volume (5) and within the damping volume (5) by means of a pipe switch (11) to the damping volume (5) is evident and can be closed again and that - On the intake pipe (4) in the damping volume (5), an open branch pipe (12) with a given length is returned in parallel to the direction (2) of the air flow in the damping volume (5).
3) Ansaugvorrichtung nach Anspruch 2, dadurch gekennzeich¬ net, daß3) suction device according to claim 2, characterized gekennzeich¬ net that
- zwischen dem Luftfilter (3) und dem Dämpfungsvolumen (5) ein am Eingang des Dämpfungsvolumens (5) verschließbarer Zusatzkanal (8) für die Ansaugluft angeordnet ist.- Between the air filter (3) and the damping volume (5) is arranged at the entrance of the damping volume (5) closable additional channel (8) for the intake air.
4) Ansaugvorrichtung nach Anspruch 3, dadurch gekennzeich¬ net, daß4) suction device according to claim 3, characterized gekennzeich¬ net that
- eine Umschaltung der wirksamen Größe des DämpfungsVolu¬ mens (5) , in Abhängigkeit von der Drehzahl des Verbren¬ nungsmotors, in folgender Weise durchführbar ist:- The effective size of the damping volume (5) can be switched over as a function of the speed of the internal combustion engine in the following manner:
a) zur Schalldämpfung im mittleren Drehzahlbereich ist der Zusatzkanal (8) und die Rohrweiche (11) geöffnet,a) the additional duct (8) and the pipe switch (11) are open for sound absorption in the medium speed range,
b) zur variablen Schalldämpfung im gesamten Drehzahlbereich ist der Zusatzkanal (8) und die Rohrweiche (11) geschlos¬ sen, wobei die gewünschte Dämpfungscharakteristik durch die Länge des Abzweigrohres (12) bestimmbar ist,b) for variable sound absorption in the entire speed range, the additional duct (8) and the pipe switch (11) are closed, the desired damping characteristic being determinable by the length of the branch pipe (12),
c) zur Schalldämpfung im oberen Drehzahlbereich ist der Zu- satzkanal (8) geschlossen und die Rohrweiche (11) geöffnet. 5) Ansaugvorrichtung nach einem der vorhergehenden Ansprü¬ che, dadurch gekennzeichnet, daßc) for sound absorption in the upper speed range, the additional duct (8) is closed and the pipe switch (11) is opened. 5) suction device according to one of the preceding Ansprü¬ che, characterized in that
- die für die Variierung des Dämpfungsvolumens (5) notwen¬ digen Schaltvorgänge vom Hydrauliksystem eines Kraftfahr¬ zeuges in Abhängigkeit von der Drehzahl des Verbrennungsmo¬ tors aktiviert werden. - The switching processes necessary for varying the damping volume (5) are activated by the hydraulic system of a motor vehicle as a function of the speed of the combustion engine.
EP97923023A 1996-05-08 1997-05-07 Air intake system for an internal combustion engine Expired - Lifetime EP0897468B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19618432A DE19618432A1 (en) 1996-05-08 1996-05-08 Intake device for an internal combustion engine
DE19618432 1996-05-08
PCT/EP1997/002361 WO1997042408A1 (en) 1996-05-08 1997-05-07 Air intake system for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP0897468A1 true EP0897468A1 (en) 1999-02-24
EP0897468B1 EP0897468B1 (en) 2002-01-23

Family

ID=7793665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97923023A Expired - Lifetime EP0897468B1 (en) 1996-05-08 1997-05-07 Air intake system for an internal combustion engine

Country Status (11)

Country Link
US (1) US6135079A (en)
EP (1) EP0897468B1 (en)
JP (1) JP2000509461A (en)
BR (1) BR9708924A (en)
CA (1) CA2254138A1 (en)
CZ (1) CZ360898A3 (en)
DE (2) DE19618432A1 (en)
ES (1) ES2171936T3 (en)
IN (1) IN188548B (en)
WO (1) WO1997042408A1 (en)
ZA (1) ZA973820B (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10004991A1 (en) * 2000-02-04 2001-08-09 Volkswagen Ag Helmholtz resonator with variable resonance frequency for damping IC engine air intake or exhaust gas noise uses controlled stops for altering neck opening cross-sections
US20030091198A1 (en) * 2001-11-15 2003-05-15 Siemens Vdo Automotive, Inc. Active noise control system with a helmholtz resonator
DE10231238B4 (en) * 2002-07-11 2004-06-03 J. Eberspächer GmbH & Co. KG Noise damping device
US6959679B2 (en) * 2002-11-15 2005-11-01 Advanced Engine Management Inc. Air intake device for internal combustion engine
US6938601B2 (en) * 2003-05-21 2005-09-06 Mahle Tennex Industries, Inc. Combustion resonator
US7117974B2 (en) * 2004-05-14 2006-10-10 Visteon Global Technologies, Inc. Electronically controlled dual chamber variable resonator
US7793757B2 (en) * 2006-03-30 2010-09-14 Mahle International Gmbh Resonator with internal supplemental noise attenuation device
US7401590B2 (en) * 2006-10-09 2008-07-22 Harley-Davidson Motor Company Group, Inc. Active air intake for an engine
US7497196B2 (en) * 2006-12-12 2009-03-03 Gm Global Technology Operations, Inc. Intake assembly having Helmholtz resonators
US7578168B2 (en) * 2007-06-27 2009-08-25 Asml Holding N.V. Increasing gas gauge pressure sensitivity using nozzle-face surface roughness
DE102010015541A1 (en) * 2010-04-20 2011-10-20 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Air cleaner with resonator built into the air outlet
JP5685422B2 (en) * 2010-11-19 2015-03-18 本田技研工業株式会社 Cogeneration equipment
DE102011051689A1 (en) 2011-07-08 2013-01-10 Dr. Ing. H.C. F. Porsche Ag Noise transmission system
DE102011051691A1 (en) * 2011-07-08 2013-01-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Noise transmission system
FR2992025B1 (en) * 2012-06-19 2014-08-08 Peugeot Citroen Automobiles Sa METHOD FOR CONTROLLING AN AIR SUPPLY OF AN INTERNAL COMBUSTION ENGINE
DE102017012012A1 (en) 2017-12-22 2019-06-27 Mann+Hummel Gmbh Acoustic resonator of an air duct system and air duct system

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4539947A (en) * 1982-12-09 1985-09-10 Nippondenso Co., Ltd. Resonator for internal combustion engines
US4546733A (en) * 1983-03-22 1985-10-15 Nippondenso Co., Ltd. Resonator for internal combustion engines
JPH0819885B2 (en) * 1988-12-28 1996-03-04 マツダ株式会社 Engine intake system
JP3034258B2 (en) * 1989-01-24 2000-04-17 マツダ株式会社 Engine intake silencer
JPH0412161A (en) * 1990-05-01 1992-01-16 Mazda Motor Corp Intake device of engine
US5163387A (en) * 1991-10-07 1992-11-17 Siemens Automotive Limited Device for attenuating standing waves in an induction intake system
JPH05272421A (en) * 1992-03-24 1993-10-19 Mazda Motor Corp Air intake device for engine
US5377629A (en) * 1993-10-20 1995-01-03 Siemens Electric Limited Adaptive manifold tuning
US5572966A (en) * 1994-09-30 1996-11-12 Siemens Electric Limited Method and composite resonator for tuning an engine air induction system
JPH08158966A (en) * 1994-11-30 1996-06-18 Nippondenso Co Ltd Noise control device of internal combustion engine
JPH09144986A (en) * 1995-11-27 1997-06-03 Nissan Motor Co Ltd Noise absorbing duct structure
US5571242A (en) * 1995-12-26 1996-11-05 General Motors Corporation Engine airflow system and method
JP3304751B2 (en) * 1996-03-29 2002-07-22 トヨタ自動車株式会社 Intake passage structure of internal combustion engine
JP3787915B2 (en) * 1996-09-04 2006-06-21 豊田合成株式会社 Intake pipe for internal combustion engine
DE19705273C1 (en) * 1997-02-12 1998-03-05 Porsche Ag Induction system for internal combustion engine
JP3420471B2 (en) * 1997-07-22 2003-06-23 本田技研工業株式会社 Intake silencer
US5771851A (en) * 1997-07-29 1998-06-30 Siemens Electric Limited Variably tuned Helmholtz resonator with linear response controller

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9742408A1 *

Also Published As

Publication number Publication date
ZA973820B (en) 1997-11-14
JP2000509461A (en) 2000-07-25
CA2254138A1 (en) 1997-11-13
DE19618432A1 (en) 1997-11-13
ES2171936T3 (en) 2002-09-16
BR9708924A (en) 1999-08-03
CZ360898A3 (en) 1999-06-16
US6135079A (en) 2000-10-24
IN188548B (en) 2002-10-12
DE59706189D1 (en) 2002-03-14
WO1997042408A1 (en) 1997-11-13
EP0897468B1 (en) 2002-01-23

Similar Documents

Publication Publication Date Title
EP0897468A1 (en) Air intake system for an internal combustion engine
DE69702447T2 (en) EXHAUST GAS DEVICE FOR INTERNAL COMBUSTION ENGINES AND VEHICLE WITH THIS DEVICE
WO2016206915A1 (en) Exhaust-gas system
DE102005041692A1 (en) Silencer for an exhaust system
EP0902862B1 (en) Airflow device
DE102005022824A1 (en) Electronically controlled variable two-chamber resonator
DE102012112433A1 (en) Exhaust system for an internal combustion engine
DE102007021541B4 (en) Device and system for closed crankcase ventilation
EP1321639B1 (en) Silencer arrangement
EP0242797B1 (en) Intake silencer, in particular for internal-combustion engines
DE102007026416B4 (en) Device for influencing the intake noise of an internal combustion engine
DE3801153C2 (en)
EP1063406B1 (en) Piping system having a throttle valve
EP1739287B1 (en) Method for actuating a selector element in an exhaust system for a vehicle
DE10231238B4 (en) Noise damping device
DE202011001554U1 (en) Exhaust assembly for use with an internal combustion engine
DE19622235C2 (en) Intake device for an internal combustion engine
DE10062472C1 (en) Exhaust system of a motor vehicle
DE19754840A1 (en) Motor air intake silencer
DE10354699B4 (en) Exhaust silencer for internal combustion engines
DE102005004674B4 (en) Device for silencing pulsating gas flows
DE4134408A1 (en) VARIABLE INTAKE MUFFLER FOR USE IN MOTOR VEHICLES
KR100482614B1 (en) Air intake system for an internal combustion engine
DE9413493U1 (en) Device for reducing noise in internal combustion engines
DE19532751A1 (en) Silencer for induction tract of internal combustion engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19981021

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

17Q First examination report despatched

Effective date: 20010613

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB

REF Corresponds to:

Ref document number: 59706189

Country of ref document: DE

Date of ref document: 20020314

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020419

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2171936

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20050425

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20050510

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20050512

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20050517

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060507

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20061201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20060507

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20070131

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20060508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060531