EP0242797B1 - Intake silencer, in particular for internal-combustion engines - Google Patents

Intake silencer, in particular for internal-combustion engines Download PDF

Info

Publication number
EP0242797B1
EP0242797B1 EP87105625A EP87105625A EP0242797B1 EP 0242797 B1 EP0242797 B1 EP 0242797B1 EP 87105625 A EP87105625 A EP 87105625A EP 87105625 A EP87105625 A EP 87105625A EP 0242797 B1 EP0242797 B1 EP 0242797B1
Authority
EP
European Patent Office
Prior art keywords
intake
shut
intake silencer
flow cross
diffusor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87105625A
Other languages
German (de)
French (fr)
Other versions
EP0242797A1 (en
Inventor
Quang-Hue Vo
Peter-Josef Esser
Georg Gaede
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0242797A1 publication Critical patent/EP0242797A1/en
Application granted granted Critical
Publication of EP0242797B1 publication Critical patent/EP0242797B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M35/12—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

Definitions

  • the invention relates to an intake silencer, especially for internal combustion engines of the type specified in the preamble of the independent claim.
  • Such an intake silencer is known for example from FR-A-2,385,906 or the corresponding DE 2714100 C2.
  • the air supply comprises two diffusers of different dimensions. It is characteristic here that the two diffusers are connected to one another over their entire length by a gap which is dimensioned for sound absorption by interference.
  • a gap has a disadvantageous effect on the diffuser, which, with a small flow cross section and a relatively large length, serves as an oscillating tube for influencing the torque curve in the lower speed range of the internal combustion engine.
  • the wall parts delimiting the gap between the diffusers arranged diverging from the intake silencer act as sound sources.
  • the invention has for its object to design an intake silencer of the type described in such a way that the measures taken for effective damping of the intake silencer also bring about a torque-increasing effect on the internal combustion engine.
  • the core of the invention is the separate arrangement of the diffusers for mutual acoustic decoupling in combination with associated, alternately controllable shut-off elements. This gives the advantage of designing one of the two diffusers for an optimal torque curve in the lower and middle speed range of the machine and the other diffuser for a favorable power curve, with the two shut-off devices of the respective diffusers achieving correspondingly low natural resonances of the intake silencer.
  • the natural frequency of the intake silencer when air is supplied through the diffuser which acts as an undisturbed oscillating tube with a relatively small flow cross-section, can be reduced to such an extent that effective acoustic damping is advantageously achieved in a frequently used, fuel-efficient speed range of the internal combustion engine, and thus a pronounced one in a vehicle Acoustic annoyance due to the intake noise stops.
  • At least one shut-off device is equipped with a servomotor according to claim 2, which can be controlled via a preferably electronic control device.
  • a servomotor according to claim 2, which can be controlled via a preferably electronic control device.
  • an actuator it is conceivable to mechanically bring both flaps into drive connection with one another.
  • each of the flaps can be equipped with an actuator.
  • An air quantity or air mass signal, a signal derived from the intake manifold vacuum or the intake manifold vacuum directly as well as a signal of the speed of the internal combustion engine can serve as manipulated variables.
  • shut-off devices for controlling air collectors are known, the separately arranged air collectors being connected to combustion chambers of the internal combustion engine via combustion chambers of different dimensions. In contrast to the alternate control according to the invention, however, these shut-off devices are opened and closed one after the other.
  • a schematically and partially sectioned intake silencer 1 comprises a housing 2 which delimits a damping chamber 3.
  • An air filter insert 4 is arranged in the damping chamber 3. Downstream of the air filter insert 4, the intake silencer 1 is in an air-conducting connection via an opening 5 in the housing 2 to the remaining intake system, not shown, of an internal combustion engine.
  • a flow cross section of the diffusers 6 and 7 is understood to mean an average intake cross section AM.
  • the mean flow cross sections A m6 and A M7 are determined from the inflow-side cross sections A 61 and A71 and from the chamber-side cross sections A 62 and A 72 according to the formula
  • the sizes of the different flow cross sections A M6 and A M7 are selected so that the natural resonance frequency f 06 of the diffuser 6 is in a low speed range of the internal combustion engine.
  • the intake noise damper 1 thus achieves damping of the intake noise in a speed range frequently used because of the relatively high torque curve during operation of the internal combustion engine or the vehicle. With the simultaneous or parallel use of both diffusers 6 and 7 over the entire operating range of the internal combustion engine, an earlier damping of the intake noise is achieved compared to an intake damper with only one diffuser.
  • the damping of the intake noise can be shifted to low engine speeds by equipping each diffuser 8, 9 of an intake silencer 10 with a shut-off device 11 or 12, the shut-off devices 11 and 12 being controlled as a function of load and speed.
  • Each of the shut-off devices 11, 12 is equipped with a servomotor 13, 14 which is symbolized by dashed lines and which can be controlled via a preferably electronic control device 15.
  • controllable flaps 11 and 12 it is possible to supply the intake air for the internal combustion engine via one or the other of the diffusers 8 and 9 of different sizes to the internal combustion engine.
  • the flap 11 of the diffuser 8 When the internal combustion engine is operating in the lower speed range, the flap 11 of the diffuser 8 is open, which has a smaller flow cross section relative to the diffuser 9.
  • the geometrical dimensions of the diffuser 8 are coordinated for this speed range in such a way that a favorable torque curve is achieved in this speed range at full load.
  • the flap 12 of the diffuser 9 having a larger flow cross section is opened, while the flap 11 of the diffuser is closed and this diffuser is thus switched off.
  • each of the diffusers 8, 9 can be optimally designed according to its area of use in terms of its geometric dimensions with regard to the torque or with respect to the power. Due to the different geometrical dimensions arising further two different Eigenresonanzfre- Uenzen q f o8 and f oa, where f oa is very small. In this way, a high damping effect is achieved in the intake silencer 10 even at low speeds, and the level of the intake noise is thus kept low.
  • 16 denotes part of an intake system of the internal combustion engine, not shown.
  • a device 17 of a mixture formation system is operatively connected to the part of the intake system 16.
  • the device 17 is an air flow meter, which supplies a signal to the electronic control device 15 via a line 18.
  • This air volume signal on line 18 is processed with a speed signal of the internal combustion engine on line 19 in control device 15 to produce an output signal to an amplifier 20 for controlling one or the other servomotor 13, 14.
  • the device 17 can be a sensor which emits a signal corresponding to the respective intake manifold vacuum to the control device 15 via the line 18, the further signal processing taking place analogously to the control described above.
  • Fig. 3 shows an intake silencer 10 with pneumatic servomotors 21 and 22 for the shut-off devices 11 and 12.
  • the servomotors 21 and 22 are actuated via the intake manifold vacuum downstream of the device 17 designed as a carburetor in part 16 of the intake system of the internal combustion engine, not shown.
  • a controllable valve 26 is arranged between a suction-side vacuum line 23 and control lines 24 and 25 to the servomotors 21 and 22.
  • the valve 26 is controlled by an electronic control device 27, which is supplied with signals about the throttle valve position and the speed of the internal combustion engine.

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)

Description

Die Erfindung bezieht sich auf einen Ansauggeräuschdämpfer, insbesondere für Brennkraftmaschinen der im Oberbegriff des unabhängigen Patentanspruches angegebenen Bauart.The invention relates to an intake silencer, especially for internal combustion engines of the type specified in the preamble of the independent claim.

Ein derartiger Ansauggeräuschdämpfer ist beispielsweise aus der FR-A-2,385,906 bzw. der entsprechenden DE 2714100 C2 bekannt. Bei diesem bekannten Ansauggeräuschdämpfer umfaßt die Luftzuführung zwei Diffusoren von unterschiedlicher Dimensionierung. Kennzeichnend hierbei ist, daß die beiden Diffusoren über ihre gesamte Länge durch einen zur Schalldämpfung durch Interferenz bemessenen Spalt miteinander verbunden sind. Bei den miteinander akkustisch gekoppelten Diffusoren wirkt sich jedoch ein derartiger Spalt nachteilig auf den Diffusor aus, der mit geringem Strömungsquerschnitt bei relativ großer Länge als Schwingrohr zur Beeinflussung des Drehmomentverlaufes im unteren Drehzahlbereich der Brennkraftmaschine dient. Weiter wirken die zwischen den Zum Ansauggeräuschdämpfer divergierend angeordneten Diffusoren den Spalt begrenzenden Wandteilen als Schallquellen.Such an intake silencer is known for example from FR-A-2,385,906 or the corresponding DE 2714100 C2. In this known intake silencer, the air supply comprises two diffusers of different dimensions. It is characteristic here that the two diffusers are connected to one another over their entire length by a gap which is dimensioned for sound absorption by interference. In the case of the acoustically coupled diffusers, however, such a gap has a disadvantageous effect on the diffuser, which, with a small flow cross section and a relatively large length, serves as an oscillating tube for influencing the torque curve in the lower speed range of the internal combustion engine. Furthermore, the wall parts delimiting the gap between the diffusers arranged diverging from the intake silencer act as sound sources.

Der Erfindung liegt die Aufgabe zugrunde, einen Ansauggeräuschdämpfer der eingangs beschriebenen Bauart so zu gestalten, daß die für eine wirkungsvolle Dämpfung des Ansauggeräuschdämpfers getroffenen Maßnahmen zugleich eine drehmomentsteigernde Wirkung an der Brennkraftmaschine bewirken.The invention has for its object to design an intake silencer of the type described in such a way that the measures taken for effective damping of the intake silencer also bring about a torque-increasing effect on the internal combustion engine.

Diese Aufgabe wird mit den kennzeichnenden Merkmalen des Patentanspruches 1 gelöst.This object is achieved with the characterizing features of patent claim 1.

Kern der Erfindung ist die zur gegenseitigen akkustischen Entkoppelung getroffene gesonderte Anordnung der Diffusoren in Kombination mit zugeordneten, wechselweise ansteuerbaren Absperrorganen. Dies ergibt den Vorteil, einen der beiden Diffusoren für einen optimalen Drehmomentverlauf im unteren und mittleren Drehzahlbereich der Maschine und den anderen Diffusor auf günstigen Leistungsverlauf hin auszubilden, wobei mit den beiden Absperrorganen der jeweiligen Diffusoren entsprechend niedrige Eigenresonanzen des Ansauggeräuschdämpfers erzielt werden. Insbesondere kann die Eigenfrequenz des Ansauggeräuschdämpfers bei Luftzufuhr über den als ungestörtes Schwingrohr von relativ kleinem Strömungsquerschnitt wirkenden Diffusor soweit abgesenkt werden, daß in vorteilhafter Weise eine wirkungsvolle akkustische Dämpfung in einem häufig genutzten, verbrauchsgünstigen Drehzahbereich der Brennkraftmaschine erzielt ist, und somit in einem Fahrzeug eine ausgeprägte akkustische Belästung durch das Ansauggeräusch in Fortfall kommt.The core of the invention is the separate arrangement of the diffusers for mutual acoustic decoupling in combination with associated, alternately controllable shut-off elements. This gives the advantage of designing one of the two diffusers for an optimal torque curve in the lower and middle speed range of the machine and the other diffuser for a favorable power curve, with the two shut-off devices of the respective diffusers achieving correspondingly low natural resonances of the intake silencer. In particular, the natural frequency of the intake silencer when air is supplied through the diffuser, which acts as an undisturbed oscillating tube with a relatively small flow cross-section, can be reduced to such an extent that effective acoustic damping is advantageously achieved in a frequently used, fuel-efficient speed range of the internal combustion engine, and thus a pronounced one in a vehicle Acoustic annoyance due to the intake noise stops.

Zur Erzielung eines raschen Wechsels von einem Diffusor auf den anderen entsprechend einem Lastwechsel der Brennkraftmaschine ist nach Anspruch 2 mindestens ein Absperrorgan mit einem Stellmotor ausgerüstet, der über eine vorzugsweise elektronische Steuereinrichtung ansteuerbar ist. Bei Verwendung eines Stellmotores ist es denkbar, beide Klappen mechanisch miteinander in Antriebsverbindung zu bringen. Für eine feinfühlig arbeitende Betätigung der Klappen kenn jede der Klappen mit einem Stellmotor ausgerüstet sein. Als Stellgrößen können ein Luftmengen- oder Luftmassensignal, ein vom Saugrohrunterdruck abgeleitetes Signal oder der Saugrohrunterdruck direkt sowie ein Signal der Drehzahl der Brennkraftmaschine dienen.In order to achieve a rapid change from one diffuser to the other in accordance with a load change of the internal combustion engine, at least one shut-off device is equipped with a servomotor according to claim 2, which can be controlled via a preferably electronic control device. When using an actuator, it is conceivable to mechanically bring both flaps into drive connection with one another. For a sensitive operation of the flaps, each of the flaps can be equipped with an actuator. An air quantity or air mass signal, a signal derived from the intake manifold vacuum or the intake manifold vacuum directly as well as a signal of the speed of the internal combustion engine can serve as manipulated variables.

Zwar sind aus der DE-A-34 34 476 für eine Ansauganlage einer Brennkraftmaschine über Stellmotore betätigbare Absperrorgane zur Steuerung von Luftsammlern bekannt, wobei die getrennt angeordneten Luftsammler über unterschiedlich dimensionierte Ansaugkanäle mit Brennräumen der Brennkraftmaschine in Verbindung stehen. Diese Absperrorgane werden jedoch im Gegensatz zur erfindungsgemäßen wechselweisen Steuerung nacheinander auf- und zugesteuert.From DE-A-34 34 476 for an intake system of an internal combustion engine actuable shut-off devices for controlling air collectors are known, the separately arranged air collectors being connected to combustion chambers of the internal combustion engine via combustion chambers of different dimensions. In contrast to the alternate control according to the invention, however, these shut-off devices are opened and closed one after the other.

Die Erfindung ist anhand von in der Zeichnung dargestellten Ausführungsbeispielen beschrieben. Es zeigen:

  • Fig. 1 ein principielles Beispiel eines Ansauggeräuschdämfers mit parallelgeschalteten Diffusoren, wobei hier die Absperrorgane nicht gezeigt sind.
  • Fig. 2 und 3 jeweils ein Ausführungsbeispiel eines Ansauggeräuschdämpfers mit abschaltbaren Diffusoren und einer der jeweiligen Gemischbildungseinrichtung entsprechenden Steuereinrichtung für die Absperrorgane der Diffusoren.
The invention is described with reference to exemplary embodiments shown in the drawing. Show it:
  • Fig. 1 shows a basic example of an intake silencer with parallel-connected diffusers, the shut-off elements not being shown here.
  • 2 and 3 each show an embodiment of an intake silencer with diffusers that can be switched off and a control device for the shut-off elements of the diffusers that corresponds to the respective mixture formation device.

Ein schematisch und teilweise geschnitten dargestellter Ansauggeräuschdämpfer 1 umfaßt ein Gehäuse 2, das eine Dämpfungskammer 3 begrenzt. In der Dämpfungskammer 3 ist ein Luftfiltereinsatz 4 angeordnet. Stromab des Luftfiltereinsatzes 4 steht der Ansauggeräuschdämpfer 1 über eine Öffnung 5 im Gehäuse 2 mit dem übrigen, nicht dargestellten Ansaugsystem einer Brennkraftmaschine in luftführender Verbindung.A schematically and partially sectioned intake silencer 1 comprises a housing 2 which delimits a damping chamber 3. An air filter insert 4 is arranged in the damping chamber 3. Downstream of the air filter insert 4, the intake silencer 1 is in an air-conducting connection via an opening 5 in the housing 2 to the remaining intake system, not shown, of an internal combustion engine.

Stromauf des Luftfiltereinsatzes 4 wird die Ansaugluft aus der freien Umgebung über unterschiedlich große Diffusoren 6 und 7 der Dämpfungskammer 3 zugeführt. Die Diffusoren 6 und 7 sind etwa von gleicher Länge und weisen, relativ zueinander, verschieden große Strömungsquerschnitte auf. Als Strömungsquerschnitt der Diffusoren 6 und 7 wird ein mittlerer Ansaugquerschnitt AM verstanden. Die mittleren Strömungsquerschnitte Am6 und AM7 werden aus den einströmseitigen Querschnitten A61 und A71 sowie aus den kammerseitigen Querschnitten A62 und A72 bestimmt nach der Formel

Figure imgb0001
Upstream of the air filter insert 4, the intake air from the free environment is supplied to the damping chamber 3 via diffusers 6 and 7 of different sizes. The diffusers 6 and 7 are of approximately the same length and, in relation to one another, have differently large flow cross sections. A flow cross section of the diffusers 6 and 7 is understood to mean an average intake cross section AM. The mean flow cross sections A m6 and A M7 are determined from the inflow-side cross sections A 61 and A71 and from the chamber-side cross sections A 62 and A 72 according to the formula
Figure imgb0001

Allgemein sind bei einem Ausauggeräuschdämpfer mit einem Diffusor dessen Länge und dessen mittlerer Strömungsquerschnitt sowie das Volumen der Dämpfungskammer des Ansauggeräuschdämpfers für die Eigenresonanzfrequenz fo wesentlich bestimmend. Bei Konstanthaltung zweier der vorgenannnten Größen und einer Aufteilung der dritten Größe nach unterschiedlichen Werten können mit der Anzahl der Aufteilungen nach unterschiedlichen Werten ebensoviele Eigenresonanzfrequenzen fo für einen Ansauggeräuschdämpfer erzielt werden. Der Ansauggeräuschdämpfer 1 mit den Diffusoren 6 und 7 von unterschiedlichen, mittleren Strömungsquerschnitten AM6 und AM7 weist demnach zwei Eigenresonanzfrequenzen f06 und f07 auf. Die Größen der unterschiedlichen Strömungsquerschnitte AM6 und AM7 sind so gewählt, daß die Eigenresonanzfrequenz f06 des Diffusors 6 in einem niedrigen Drehzahlbereich der Brennkraftmaschine liegt. Damit wird mit dem Ansauggeräuschdämpfer 1 eine Dämpfung des Ansauggeräusches in einem wegen des relativ hohen Drehmomentverlaufes beim Betrieb der Brennkraftmaschine bzw. des Fahrzeuges häufig benutzten Drehzahlbereich erzielt. Mit der gleichzeitigen bzw. parallelen Benutzung beider Diffusoren 6 und 7 über den gesamten Betriebsbereich der Brennkraftmaschine wird gegenüber einem Ansaugdämpfer mit nur einem Diffusor damit eine früher einsetzende Dämpfung des Ansauggeräusches erreicht.In general, in the case of an exhaust noise damper with a diffuser, its length and its mean flow cross section, as well as the volume of the damping chamber of the intake noise damper , are essential for the natural resonance frequency f o . If two of the aforementioned sizes are kept constant and the third size is divided according to different ones Values can be achieved with the number of divisions according to different values, as many natural resonance frequencies f o for an intake silencer. The intake silencer 1 with the diffusers 6 and 7 of different, average flow cross sections A M6 and A M7 accordingly has two natural resonance frequencies f 06 and f 07 . The sizes of the different flow cross sections A M6 and A M7 are selected so that the natural resonance frequency f 06 of the diffuser 6 is in a low speed range of the internal combustion engine. The intake noise damper 1 thus achieves damping of the intake noise in a speed range frequently used because of the relatively high torque curve during operation of the internal combustion engine or the vehicle. With the simultaneous or parallel use of both diffusers 6 and 7 over the entire operating range of the internal combustion engine, an earlier damping of the intake noise is achieved compared to an intake damper with only one diffuser.

Die Dämpfung des Ansauggeräusches kann nach niederen Drehzahlen der Brennkraftmaschine dadurch verschoben werden, daß jeder Diffusor 8, 9 eines Ansauggeräuschdämpfers 10 jeweils mit einem Absperrorgan 11 bzw. 12 ausgerüstet ist, wobei die Absperrorgäne 11 und 12 last- und drehzahlabhängig gesteuert werden. Jedes der Absperrogane 11, 12 ist mit einem durch gestrichelte Linien versinnbildlichten Stellmotor 13, 14 ausgerüstet, der über eine vorzugsweise elektronische Steuereinrichtung 15 ansteuerbat ist.The damping of the intake noise can be shifted to low engine speeds by equipping each diffuser 8, 9 of an intake silencer 10 with a shut-off device 11 or 12, the shut-off devices 11 and 12 being controlled as a function of load and speed. Each of the shut-off devices 11, 12 is equipped with a servomotor 13, 14 which is symbolized by dashed lines and which can be controlled via a preferably electronic control device 15.

Mit den steuerbaren Klappen 11 und 12 ist es möglich, die Ansaugluft für die Brennkraftmaschine über den einen oder den anderen der unterschiedlich großen Diffusoren 8 und 9 der Brennkraftmaschine zuzuführen. Beim Betrieb der Brennkraftmaschine im unteren Drehzahlbereich ist die Klappe 11 des Diffusors 8 geöffnet, der relativ zum Diffusor 9 einen kleineren Strömungsquerschnitt aufweist. Der Diffusor 8 ist für diesen Drehzahlbereich in seinen geometrischen Abmessungen so abgestimmt, daß in diesem Drehzahlbereich bei Vollast ein günstiger Drehmomentverlauf erzielt wird. Bei Betrieb der Brennkraftmaschine im oberen Drehzahlbereich wird die Klappe 12 des einen größeren Strömungsquerschnitt aufweisenden Diffusors 9 geöffnet, während die Klappe 11 des Diffusors geschlossen wird und somit dieser Diffusor abgeschaltet ist. Durch den getrennten Betrieb der Diffusoren 8 und 9 kann jeder der Diffusoren 8, 9 entsprechend seinem Einsatzbereich in seinen geometrischen Abmessungen bezüglich des Drehmomentes bzw. bezüglich der Leistung optimal ausgebildet werden. Durch die unterschiedlichen geometrischen Abmessungen ergeben sich ferner zwei unterschiedliche Eigenresonanzfre- quenzen fo8 und foa, wobei foa sehr klein ist. Damit wird bei dem Ansauggeräuschdämpfer 10 schon ab kleinen Drehzahlen eine hohe Dämpfungswirkung erreicht, und damit der Pegel des Ansauggeräusches niedrig gehalten.With the controllable flaps 11 and 12, it is possible to supply the intake air for the internal combustion engine via one or the other of the diffusers 8 and 9 of different sizes to the internal combustion engine. When the internal combustion engine is operating in the lower speed range, the flap 11 of the diffuser 8 is open, which has a smaller flow cross section relative to the diffuser 9. The geometrical dimensions of the diffuser 8 are coordinated for this speed range in such a way that a favorable torque curve is achieved in this speed range at full load. When the internal combustion engine is operating in the upper speed range, the flap 12 of the diffuser 9 having a larger flow cross section is opened, while the flap 11 of the diffuser is closed and this diffuser is thus switched off. Due to the separate operation of the diffusers 8 and 9, each of the diffusers 8, 9 can be optimally designed according to its area of use in terms of its geometric dimensions with regard to the torque or with respect to the power. Due to the different geometrical dimensions arising further two different Eigenresonanzfre- Uenzen q f o8 and f oa, where f oa is very small. In this way, a high damping effect is achieved in the intake silencer 10 even at low speeds, and the level of the intake noise is thus kept low.

In Fig. 2 ist mit 16 ein Teil einer Ansauganlage der nicht gezeigten Brennkraftmaschine bezeichnet. Mit dem Teil der Ansauganlage 16 in Wirkverbindung steht ein Gerät 17 einer Gemischbildungsanlage. Bei einer Brennkraftmaschine mit elektronischer Einspritzung ist das Gerät 17 ein Luftmengenmesser, der über eine Leitung 18 ein Signal an die elektronische Steuereinrichtung 15 liefert. Dieses Luftmengensignal auf der Leitung 18 wird mit einem Drehzahl-Signal der Brennkraftmaschine auf einer Leitung 19 in der Steuereinrichtung 15 verarbeitet zu einem Ausgangssignal an einen Verstärker 20, zur Ansteuerung des einen oder anderen Stellmotors 13, 14.In Fig. 2, 16 denotes part of an intake system of the internal combustion engine, not shown. A device 17 of a mixture formation system is operatively connected to the part of the intake system 16. In an internal combustion engine with electronic injection, the device 17 is an air flow meter, which supplies a signal to the electronic control device 15 via a line 18. This air volume signal on line 18 is processed with a speed signal of the internal combustion engine on line 19 in control device 15 to produce an output signal to an amplifier 20 for controlling one or the other servomotor 13, 14.

Erfolgt bei einer Brennkraftmaschine die Gemischbildung über einen Vergaser, so kann das Gerät 17 ein Sensor sein, der ein dem jeweiligen Saugrohrunterdruck entsprechendes Signal über die Leitung 18 an die Steuereinrichtung 15 abgibt, wobei die weitere Signalverarbeitung analog zur vorbeschriebenen Steuerung abläuft.If the mixture is formed in an internal combustion engine via a carburetor, the device 17 can be a sensor which emits a signal corresponding to the respective intake manifold vacuum to the control device 15 via the line 18, the further signal processing taking place analogously to the control described above.

Fig. 3 zeigt einen Ansauggeräuschdämpfer 10 mit pneumatischen Stellmotoren 21 und 22 für die Absperrorgane 11 und 12. Die Stellmotore 21 und 22 werden über den Saugrohrunterdruck stromab des als Vergaser ausgebildeten Gerätes 17 in dem Teil 16 der nicht weiter gezeigten Ansauganlage der Brennkraftmaschine betätigt. Zwischen einer ansaugseitigen Unterdruckleitung 23 und Steuerleitungen 24 und 25 zu den Stellmotoren 21 und 22 ist ein steuerbares Ventil 26 angeordnet. Das Ventil 26 wird von einer elektronischen Steuereinrichtung 27 angesteuert, die mit Signalen über die Drosselklappenstellung und die Drehzahl der Brennkraftmaschine versorgt wird.Fig. 3 shows an intake silencer 10 with pneumatic servomotors 21 and 22 for the shut-off devices 11 and 12. The servomotors 21 and 22 are actuated via the intake manifold vacuum downstream of the device 17 designed as a carburetor in part 16 of the intake system of the internal combustion engine, not shown. A controllable valve 26 is arranged between a suction-side vacuum line 23 and control lines 24 and 25 to the servomotors 21 and 22. The valve 26 is controlled by an electronic control device 27, which is supplied with signals about the throttle valve position and the speed of the internal combustion engine.

Claims (2)

1. An intake silencer, in particular for internal- combustion engines, having a housing (2) defining a damping chamber (3) and two duffusors (8, 9) feeding the intake air from the free surroundings to the damping chamber (3) and widening towards the damping chamber (3), of which diffusors one has a large mean flow cross-section in comparison with the other diffusor, the two diffusors being arranged with spacing from one another and opening with spacing from one another into the damping chamber (3), characterised in that the diffusors (8, 9) are acoustically decoupled from one another and have approximately equal lengths, and in that in each diffusor (8, 9) a shut-off element (11, 12) is arranged and the shut-off elements (11, 12) are alternately controllable in dependence upon load and rotation rate in a manner such that, in the lower rotation rate range, the flap (11) in the diffusor (8) opens with small mean flow cross-section and closes in the upper rotation rate range, and the flap (12) in the diffusor (9) opens with great mean flow cross-section in the upper rotation rate range.
2. An intake silencer according to Claim 1, characterised in that at least one shut-off element (11,12) is in drive connection with a servo-motor (13,14; 21, 22) which is actuatable by means of an electronic and/or pneumatic control apparatus (15; 26, 27).
EP87105625A 1986-04-24 1987-04-15 Intake silencer, in particular for internal-combustion engines Expired - Lifetime EP0242797B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863613828 DE3613828A1 (en) 1986-04-24 1986-04-24 INTAKE MUFFLER, IN PARTICULAR FOR INTERNAL COMBUSTION ENGINES
DE3613828 1986-04-24

Publications (2)

Publication Number Publication Date
EP0242797A1 EP0242797A1 (en) 1987-10-28
EP0242797B1 true EP0242797B1 (en) 1990-12-19

Family

ID=6299402

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87105625A Expired - Lifetime EP0242797B1 (en) 1986-04-24 1987-04-15 Intake silencer, in particular for internal-combustion engines

Country Status (3)

Country Link
EP (1) EP0242797B1 (en)
DE (2) DE3613828A1 (en)
ES (1) ES2019320B3 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19615917A1 (en) * 1996-04-22 1997-10-30 Wolf Woco & Co Franz J Intake silencer and motor vehicle
EP1186768A2 (en) 2000-09-05 2002-03-13 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Air filter for a multi-cylinder internal combustion engine
US6705272B2 (en) 1999-10-26 2004-03-16 Filterwerk Mann & Hummel Gmbh Air intake system with an air filter
DE102007026416B4 (en) * 2007-06-06 2014-09-04 Audi Ag Device for influencing the intake noise of an internal combustion engine

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3801153A1 (en) * 1987-01-24 1988-08-04 Mann & Hummel Filter Device for the silencing of intake noises of internal combustion engines
DE19811051B4 (en) 1998-03-13 2014-01-02 Mann + Hummel Gmbh Air intake device for an internal combustion engine
DE19926135A1 (en) * 1999-06-09 2000-12-14 Volkswagen Ag Air intake system for an internal combustion engine
DE10055399A1 (en) * 1999-11-20 2001-05-23 Mann & Hummel Filter Controlling sound in air inlet manifold of engine, employs valve closing at least partially, at given periodic intervals when little or no air is transferred
GB2389150B (en) 2001-09-07 2004-08-25 Avon Polymer Prod Ltd Noise and vibration suppressors
EP1335124B1 (en) * 2002-02-09 2004-12-29 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Air filter for a combustion engine
DE102011117639A1 (en) * 2011-11-04 2013-05-08 Audi Ag Motor vehicle has suction device for internal combustion engine of motor vehicle, where suction device has two suction lines, and latter suction line has smaller flow resistance than former suction line

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE734253C (en) * 1939-02-05 1943-04-12 Knecht Alfred Wet air cleaner combined with a noise damper
GB789180A (en) * 1955-05-26 1958-01-15 Coopers Mech Joints Improvements in or relating to combined gas filters and silencers
DE1027464B (en) * 1957-03-26 1958-04-03 Alfred Knecht Air purifier and intake silencer
DE1838112U (en) * 1961-06-19 1961-09-21 Bayerische Motoren Werke Ag INTAKE SILENCER AND AIR FILTER FOR COMBUSTION MACHINES.
FR1308738A (en) * 1961-09-29 1962-11-09 Polycarbure Self-adjusting resonance expansion chamber according to the frequency of the pulsations, arranged on the pulsating flow path of fluids, and its industrial applications
DE2714100C2 (en) * 1977-03-30 1985-05-02 Volkswagenwerk Ag, 3180 Wolfsburg Air intake for an internal combustion engine
US4546733A (en) * 1983-03-22 1985-10-15 Nippondenso Co., Ltd. Resonator for internal combustion engines
DE3434476A1 (en) * 1984-09-20 1986-02-27 Bayerische Motoren Werke AG, 8000 München Mixture-compressing, applied-ignition reciprocating-piston internal combustion engine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19615917A1 (en) * 1996-04-22 1997-10-30 Wolf Woco & Co Franz J Intake silencer and motor vehicle
US6705272B2 (en) 1999-10-26 2004-03-16 Filterwerk Mann & Hummel Gmbh Air intake system with an air filter
EP1186768A2 (en) 2000-09-05 2002-03-13 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Air filter for a multi-cylinder internal combustion engine
DE10043532A1 (en) * 2000-09-05 2002-03-21 Porsche Ag Air filter unit for multicylinder IC engine for motor vehicles has air flowing against low pressure from raw air chambers through air filters into clean air chamber and engine feed pipe
US6726737B2 (en) 2000-09-05 2004-04-27 Dr. Ing. H.C.F. Porsche Ag Air filter arrangement for a multi-cylinder combustion engine
DE10043532B4 (en) * 2000-09-05 2010-11-04 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Air filter device for a multi-cylinder internal combustion engine
DE102007026416B4 (en) * 2007-06-06 2014-09-04 Audi Ag Device for influencing the intake noise of an internal combustion engine

Also Published As

Publication number Publication date
DE3766743D1 (en) 1991-01-31
EP0242797A1 (en) 1987-10-28
ES2019320B3 (en) 1991-06-16
DE3613828A1 (en) 1987-10-29

Similar Documents

Publication Publication Date Title
DE3416950C2 (en)
EP0242797B1 (en) Intake silencer, in particular for internal-combustion engines
DE2926373A1 (en) EXHAUST Bypass Valve Assembly
DE4229110C1 (en) Device for the temporary storage and metered feeding of volatile fuel components located in the free space of a tank system into the intake pipe of an internal combustion engine
DE68905179T2 (en) AIR INLET SYSTEM FOR A MULTI-CYLINDER INTERNAL COMBUSTION ENGINE.
DE10212596A1 (en) Variable intake device for a multi-cylinder internal combustion engine
DE10310487A1 (en) Noise transmission device for automobile with diesel engine or direct injection petrol engine has housing coupled to engine air intake containing throttle element and partition wall incorporating flap element
DE102008029381A1 (en) Arrangement for air filter and membrane carburetor for preparing fuel-air mixture for two stroke engine, particularly as driving engine, has membrane carburetor that is connected with clean air side of air filter over suction channel
EP0897468B1 (en) Air intake system for an internal combustion engine
DE2454512C3 (en) Exhaust gas recirculation device for internal combustion engines
DE3901627C2 (en) Carburetor with a device for idle adjustment
EP1152132B1 (en) Ducting system with electromechanical converter producing a correction noise
EP0490104B1 (en) Method of controlling the air admission for an internal combustion engine
EP0741238B1 (en) Air flow control device for a turbocharged internal combustion engine
EP1049859B1 (en) Suction system for supplying an internal combustion engine with combustion air
DE3435028A1 (en) AIR SUCTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE
EP1063406B1 (en) Piping system having a throttle valve
DE2451148C3 (en) Exhaust gas recirculation device in internal combustion engines
DE10208051B4 (en) Diaphragm carburettor for a combustion engine working with a rinse aid
DE10320857A1 (en) IC engine with direct fuel injection has ventilation pipe for crankcase controlled by throttle of air intake unit for effective ventilation of engine housing
DE4113248C2 (en)
DE69200167T2 (en) Air intake device for an internal combustion engine.
DE2249733A1 (en) INTAKE SYSTEM FOR COMBUSTION MACHINES
DE3033679C2 (en) Four-stroke internal combustion engine
DE3128604C2 (en) 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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE ES FR GB IT LI SE

17P Request for examination filed

Effective date: 19880407

17Q First examination report despatched

Effective date: 19890510

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE ES FR GB IT LI SE

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3766743

Country of ref document: DE

Date of ref document: 19910131

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

ITTA It: last paid annual fee
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: SE

Payment date: 19920402

Year of fee payment: 6

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

Ref country code: CH

Payment date: 19920406

Year of fee payment: 6

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

Ref country code: GB

Payment date: 19920414

Year of fee payment: 6

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

Ref country code: ES

Payment date: 19920415

Year of fee payment: 6

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

Ref country code: FR

Payment date: 19920429

Year of fee payment: 6

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

Ref country code: GB

Effective date: 19930415

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

Ref country code: SE

Effective date: 19930416

Ref country code: ES

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

Effective date: 19930416

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

Ref country code: LI

Effective date: 19930430

Ref country code: CH

Effective date: 19930430

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

Effective date: 19930415

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

Ref country code: FR

Effective date: 19931229

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 87105625.5

Effective date: 19931110

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990301

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050415

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

Ref country code: DE

Payment date: 20060524

Year of fee payment: 20