EP0834011B1 - Silencieux d'aspiration pour moteur a combustion interne - Google Patents

Silencieux d'aspiration pour moteur a combustion interne Download PDF

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Publication number
EP0834011B1
EP0834011B1 EP97920737A EP97920737A EP0834011B1 EP 0834011 B1 EP0834011 B1 EP 0834011B1 EP 97920737 A EP97920737 A EP 97920737A EP 97920737 A EP97920737 A EP 97920737A EP 0834011 B1 EP0834011 B1 EP 0834011B1
Authority
EP
European Patent Office
Prior art keywords
intake
intake pipe
resonator
pipe
intake silencer
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
EP97920737A
Other languages
German (de)
English (en)
Other versions
EP0834011B2 (fr
EP0834011A1 (fr
Inventor
Franz Josef Wolf
Udo GÄRTNER
Anton Wolf
Nicole Schrieber
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.)
Woco Industrietechnik GmbH
Original Assignee
Woco Franz Josef Wolf and Co 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
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Application filed by Woco Franz Josef Wolf and Co GmbH filed Critical Woco Franz Josef Wolf and Co GmbH
Publication of EP0834011A1 publication Critical patent/EP0834011A1/fr
Publication of EP0834011B1 publication Critical patent/EP0834011B1/fr
Application granted granted Critical
Publication of EP0834011B2 publication Critical patent/EP0834011B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M35/1216—Flow throttling or guiding by using a plurality of holes, slits, protrusions, perforations, ribs or the like; Surface structures; Turbulence generators
    • 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
    • F02M35/1266—Intake silencers ; Sound modulation, transmission or amplification using resonance comprising multiple chambers or compartments

Definitions

  • the invention relates to an intake silencer for a Internal combustion engine mentioned in the preamble of claim 1 Kind as well as a motor vehicle with an internal combustion engine and a supercharger an intake silencer.
  • Another intake silencer is from US 4,350,223 A known.
  • This intake silencer is flexible, from one Corrugated hose existing line used, which is the ambient air intake opening in the body of the motor vehicle with the Intake connector of the air filter connects.
  • This intake silencer dampens the air noise generated in the intake area within a narrow frequency band, which is on both sides of the Expands resonance frequency of the resonator.
  • the intake silencer of the example shown above show the disadvantage overall, only within one to dampen the comparatively narrow frequency band.
  • dampers stuffed with insulation material are only for systems suitable that have only moderate overpressure.
  • For one use in a charger intake line are damped with insulation Muffler unusable.
  • turbochargers are currently used for this purpose are working to this end with rotor speeds to nearly 200 000 min -1. It is understandable that turbochargers with such a high profile of requirements can only remain economically practical with compromises on manufacturing tolerances. This is the reason for the strong acoustic radiation of such turbochargers, namely the typical "turbocharger whistle" in the frequency range of around 2 - 4 kHz. The charging process, even in the intake line, once again produces clearly radiating broadband noises in the frequency band of 4 - 6 kHz, which are referred to as "hissing".
  • the invention is accordingly based on the object certainly also broadband airborne sound absorbers that can be used elsewhere, specifically, however, an intake silencer for an internal combustion engine to create that with the smallest possible and flexibly adaptable Construction volume in flexible adaptation to the specific Deployment requirements Airborne noise over a wide frequency band dampens equally effectively.
  • an intake silencer for an internal combustion engine to create that with the smallest possible and flexibly adaptable Construction volume in flexible adaptation to the specific Deployment requirements Airborne noise over a wide frequency band dampens equally effectively.
  • Intake silencer to be able to Automotive internal combustion engines generated by turbochargers and loudly emitted noise in the frequency band of around 2 - 6 kHz to dampen so that they are both outside the vehicle and inside Vehicle itself is practically imperceptible.
  • an intake silencer has the input mentioned type on the features mentioned in claim 1.
  • the intake silencer according to the invention is accordingly so built that the intake air flows through the damper, in an intake pipe that runs the entire axial length along which the Damping is effected by a single, preferably double-shell trained resonator housing is surrounded.
  • this Resonator housing is with the intake manifold in a conventional manner Provide openings that open the wall of the intake pipe on both sides enforce and the interior of the intake pipe with the interior of the resonator chambers formed in the resonator housing connects.
  • there is the intake pipe but not from a more or less thin steel sheet, but from materials such as aluminum, sintered metals, Plastics or hard rubber, which also the manufacture of the intake pipe with larger wall thicknesses without this becomes unusably heavy.
  • the wall thickness of the Intake pipe in the range of 0.6 to 5 mm, especially in the range between 1 to 3 mm inclusive.
  • the wall thickness of the Intake pipe, or the inner wall height of the opening in the wall of the Intake pipe a matter of coordination between the Cross-sectional area of the opening, the volume of the connected Resonator chamber and the width and frequency position of the to be set Resonance absorption band.
  • the opening and the resonator chamber thus form a tuned to the frequency band to be attenuated HELMHOLTZ resonator.
  • the width of the active resonance absorption frequency band that can be set in this way increases with decreasing cross-sectional area Opening.
  • the efficiency of the coupling i.e. the degree of achievable damping decreases
  • the cross-sectional area of the opening first be optimized between these two limit parameters.
  • the through the resonator housing around the perforated intake pipe The annular space formed is transverse to the axial course of the intake pipe aligned chamber walls in a sequence in the axial direction successive resonator chambers with each other different volume divided.
  • These are chamber walls expediently molded onto the resonator housing itself and enclose an intake pipe designed as an insert. Alternatively, you can however, the intake pipe is also firmly attached to this enclosing chamber walls formed and in this form as Insert part to be introduced in the resonator housing. Is crucial only that the resonator chambers formed in this way are hermetically delimited from each other.
  • the intake pipe nor the Resonator housings need to have a linear longitudinal axis, need to be designed coaxially or even rotationally symmetrical must be designed.
  • the resonance behavior of each individual the resonator chamber is only capable of vibrating Air volume determined in terms of its resonance frequency, and not in that all camera walls are parallel to each other, that Intake pipe runs centrally in the resonator housing or even that Chamber walls are arranged parallel to each other.
  • Air mass on each of the chambers formed in the resonator housing can act separately on each of these chambers without one of the chambers through one of the openings in the intake pipe via the Chamber partitions is bridged to the neighboring chamber.
  • the intake silencer can Invention with the smallest possible size practically everyone available Adjust installation space.
  • the neighboring chamber is tuned so that the example upper frequency of the absorption band one chamber and the lower Frequency of the absorption band of the neighboring chamber is sufficiently wide overlap.
  • Chamber volumes from chamber to chamber are basically independent of the Direction in which the intake air flows through the intake silencer. In both cases, the acoustic damping is largely the same.
  • the intake pipe and the resonator of the intake silencer can be made from any material become.
  • the suction line and the resonator housing also from the same material, because the resonator housing shell has practically no radiation. Also don't need any additional Damping materials to be used to radiate the Prevent noise from the resonator housing.
  • the intake silencer of the invention is made from heat-resistant, preferably fiber-reinforced plastic Hard rubber or from porous sintered materials or porous Materials, especially made of aluminum.
  • the geometric shape of the individual opening is basically without, at least without any significant influence on the Characteristics of the intake silencer of the invention. So they can individual resonator chambers with the inside of the intake pipe connecting openings both round, i.e. strictly cylindrical, be oval as well as oval, slit-shaped and polygonal his. However, all openings of the intake pipe are preferably formed with a circular cross section. Such an embodiment of the Intake silencer makes it easier to tune it.
  • the intake silencer is the In principle, the invention continues to be as close as possible to the pressure port of the Connect the loader, especially to flange it directly onto it or via the shortest possible acoustically insulating connection to them connect, or, preferably, directly in the pressure port of the turbocharger, for example in the German Patent DE 35 31 353 C2 for the intake manifold Intercooler known way.
  • the intake silencer 1 shown in FIG. 1 for an internal combustion engine consists of an intake pipe 2 guiding the intake air in the throughflow and one of these to form a closed annular space 2 enclosing two-shell resonator housing 4, wherein in 1 only one of the two for the sake of clarity housing shells that can be assembled to fit is shown.
  • the Intake silencer 1 is with an inlet port 5 and a Outlet connector 6 for switching on in the intake line of the Internal combustion engine equipped. It is for the better Description of the invention in the present case, the inlet connector 5 as a single part shown the suction pipe formed, while the outlet 6 as integrally connected to the resonator housing shell shown is shown. This type of design of the connecting piece is in principle interchangeable.
  • both connecting pieces are So both the inlet connector and the outlet connector, in one piece with the resonator housing, preferably in the manner that one of the two connecting pieces on one of the two Resonator housing shells, the other on top of each other Housing shell molded or otherwise formed with this.
  • This causes that in a two-shell design of the Intake pipe as an insert in the resonator housing a prestressing closing pressure and sealing purpose at Close the resonator housing by welding, screwing or can be exercised otherwise.
  • Openings 7 are formed in the tube wall of the intake tube 2 the interior of the intake pipe 2 with the annular space 3 of the Connect resonator housing 4. Each of these openings is in cross section circular, and has a wall thickness of the intake pipe 2 in the opening area of 2 mm a diameter of 3 mm.
  • the openings 7 are arranged in the intake pipe 2 so that each of the Resonator chambers 9 connected to the interior of the intake pipe 2 is, namely with the formation of a small oscillatable air mass in the Opening in such a way that none of the camera walls is bridged, i.e. is short-circuited with one of the neighboring chambers.
  • both the distribution and the number of im Intake pipe 2 for each chamber 9 provided openings 7 from chamber to Chamber be identical. In the manner shown schematically in Fig. 1 In practice, however, this will rarely be possible because of Interior designs and sizes of the intake silencer in constructive consideration.
  • the intake pipe is within the Resonator housing 4 formed with an oval cross-section, wherein a from inlet port 5 to outlet port 6 continuous channel-like Area of the intake pipe 2 has no holes 7.
  • This serves the Purpose, moisture entrained with the intake air, for example Air humidity or oil dust, not when condensing in intake pipe 2 drip into the resonator chambers 9 through the openings 7 let, but this condensate without escaping into the resonator housing run out of the outlet nozzle 6 of the intake silencer 1 leave (it should be noted that in the representation shown in Fig. 1 the spatial position of the silencer 1 is not its installation position corresponds. This is after a rotation of that shown in Fig. 1 Intake silencer 1 by 90 ° clockwise around the longitudinal axis of the Get intake pipe 2 around).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Compressor (AREA)

Claims (10)

  1. Silencieux d'aspiration pour un moteur à combustion interne, consistant en un tuyau d'aspiration acheminant l'air d'aspiration et en un boítier formant résonateur entourant le tuyau en formant un espace annulaire fermé et comportant une tubulure d'admission et une tubulure d'évacuation, des ouvertures étant prévues dans la paroi tubulaire du tuyau d'aspiration pour relier l'espace intérieur du tuyau d'aspiration à l'espace intérieur du résonateur, une suite ou une suite axiale de plusieurs parois formant chambres (8) étant dirigées transversalement à l'axe longitudinal du tuyau d'aspiration (2) et entourant celui-ci et constituant, dans le boítier formant résonateur (4), des chambres de résonance (9) hermétiquement délimitées les unes par rapport aux autres et ayant des volumes différents, et avec une disposition telle des ouvertures (7) dans la paroi tubulaire du tuyau d'aspiration (2) que chacune des chambres de résonance (9) communique avec l'espace intérieur du tuyau d'aspiration et que, de ce fait, aucune des parois formant chambres (8) ne soit court-circuitée,
       caractérisé par un dimensionnement du volume des chambres de résonance, qui est adapté, pour chaque chambre (9) individuelle, à la position et à la largeur d'une gamme de fréquences de résonance, chaque fois prédéfinie sur le plan de la conception pour la chambre concernée, ainsi que par un dimensionnement correspondant de l'aire de la section transversale de l'ouverture (7) et de l'épaisseur de paroi, correspondant à la hauteur de paroi de l'ouverture (7), du tuyau d'aspiration (2) dans la zone de l'ouverture (7) correspondante.
  2. Silencieux d'aspiration selon la revendication 1,
       caractérisé par une forme cylindrique circulaire des ouvertures (7) situées dans la paroi tubulaire du tuyau d'aspiration (2).
  3. Silencieux d'aspiration selon l'une des revendications 1 ou 2,
       caractérisé par une disposition telle des ouvertures (7), situées dans la paroi tubulaire du tuyau d'aspiration, que chacune des chambres de résonance (9) communique, par un nombre identique d'ouvertures, avec l'espace intérieur du tuyau d'aspiration (2).
  4. Silencieux d'aspiration selon l'une des revendications 1 à 3,
       caractérisé par une section transversale ovale ou ovale aplatie du tuyau d'aspiration (2).
  5. Silencieux d'aspiration selon l'une des revendications 1 à 4,
       caractérisé par une partie de paroi réalisée, sans ouvertures, de manière continue depuis la tubulure d'admission (5) jusqu'à la tubulure d'évacuation (6) dans la zone de fond du tuyau d'aspiration (2), par rapport à la position de montage, selon les prescriptions, du tuyau d'aspiration (2) dans le silencieux d'aspiration (1) et du silencieux d'aspiration au niveau du moteur à combustion interne.
  6. Silencieux d'aspiration selon l'une des revendications 1 à 5,
       caractérisé par une conception en deux parties du tuyau d'aspiration (2) avec plan axial de joint ainsi que par une conception en deux parties du boítier formant résonateur (4) avec plan axial de joint.
  7. Silencieux d'aspiration selon l'une des revendications 1 à 6,
       caractérisé par la conception du tuyau d'aspiration (2) en tant qu'élément encastré dans le boítier formant résonateur (4).
  8. Silencieux d'aspiration selon l'une des revendications 1 à 7,
       caractérisé par une tubulure d'admission et une tubulure d'évacuation (6) formées d'un seul tenant sur le boítier formant résonateur.
  9. Véhicule automobile comportant un moteur à combustion interne, un compresseur à suralimentation, un refroidisseur à air de la charge, et un silencieux d'aspiration selon l'une des revendications 1 à 8,
       caractérisé par un raccordement du silencieux d'aspiration (1) entre le compresseur et le refroidisseur à air de la charge.
  10. Véhicule automobile selon la revendication 9,
       caractérisé par le raccordement du silencieux d'aspiration (1) directement derrière la tubulure de refoulement du compresseur, ou bien au niveau de celle-ci ou encore de manière intégrée à celle-ci.
EP97920737A 1996-04-22 1997-04-22 Silencieux d'aspiration pour moteur a combustion interne Expired - Lifetime EP0834011B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19615917A DE19615917A1 (de) 1996-04-22 1996-04-22 Ansaugschalldämpfer und Kraftfahrzeug
DE19615917 1996-04-22
PCT/EP1997/002038 WO1997040271A1 (fr) 1996-04-22 1997-04-22 Silencieux d'aspiration pour moteur a combustion interne

Publications (3)

Publication Number Publication Date
EP0834011A1 EP0834011A1 (fr) 1998-04-08
EP0834011B1 true EP0834011B1 (fr) 2000-05-31
EP0834011B2 EP0834011B2 (fr) 2004-10-27

Family

ID=7792036

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97920737A Expired - Lifetime EP0834011B2 (fr) 1996-04-22 1997-04-22 Silencieux d'aspiration pour moteur a combustion interne

Country Status (5)

Country Link
US (1) US5979598A (fr)
EP (1) EP0834011B2 (fr)
DE (2) DE19615917A1 (fr)
ES (1) ES2146465T5 (fr)
WO (1) WO1997040271A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002101227A1 (fr) 2001-06-13 2002-12-19 Woco Franz-Josef Wolf & Co. Gmbh Silencieux
US6983820B2 (en) 2001-09-07 2006-01-10 Avon Polymer Products Limited Noise and vibration suppressors

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DE19615917A1 (de) 1997-10-30
EP0834011B2 (fr) 2004-10-27
US5979598A (en) 1999-11-09
DE59701802D1 (de) 2000-07-06
EP0834011A1 (fr) 1998-04-08
WO1997040271A1 (fr) 1997-10-30
ES2146465T3 (es) 2000-08-01
ES2146465T5 (es) 2005-04-16

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