EP0834011A1 - Ansaugschalldämpfer und kraftfahrzeug - Google Patents
Ansaugschalldämpfer und kraftfahrzeugInfo
- Publication number
- EP0834011A1 EP0834011A1 EP97920737A EP97920737A EP0834011A1 EP 0834011 A1 EP0834011 A1 EP 0834011A1 EP 97920737 A EP97920737 A EP 97920737A EP 97920737 A EP97920737 A EP 97920737A EP 0834011 A1 EP0834011 A1 EP 0834011A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- intake
- intake pipe
- resonator
- openings
- 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.)
- Granted
Links
- 230000003584 silencer Effects 0.000 title claims abstract description 43
- 238000002485 combustion reaction Methods 0.000 claims abstract description 17
- 238000009434 installation Methods 0.000 claims description 5
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- MBYLVOKEDDQJDY-UHFFFAOYSA-N tris(2-aminoethyl)amine Chemical compound NCCN(CCN)CCN MBYLVOKEDDQJDY-UHFFFAOYSA-N 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 4
- 238000005192 partition Methods 0.000 abstract description 3
- 230000030279 gene silencing Effects 0.000 abstract 1
- 238000011144 upstream manufacturing Methods 0.000 abstract 1
- 239000003570 air Substances 0.000 description 16
- 238000013016 damping Methods 0.000 description 16
- 230000007423 decrease Effects 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 238000010521 absorption reaction Methods 0.000 description 4
- 239000006096 absorbing agent Substances 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 229920001875 Ebonite Polymers 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 239000011810 insulating material Substances 0.000 description 2
- 239000012774 insulation material Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 229920002430 Fibre-reinforced plastic Polymers 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000011151 fibre-reinforced plastic Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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 an internal combustion engine of the type mentioned in the preamble of claim 1 and a motor vehicle with an internal combustion engine and a supercharger with an intake silencer.
- FIG. 1 of this document shows a muffler combination arranged directly behind the inlet air filter, in which the intake pipe is provided with wall openings immediately behind the dust filter cartridge and is surrounded by an insulating material.
- the suction pipe is provided with an axial sequence of rows of holes arranged in a ring. Each of these rows of holes is connected to a chamber surrounding the intake pipe on the outside.
- Bell-shaped sleeves deflect the sound waves passing through one of the rows of holes from the intake air in such a way that they are directed in the opposite direction to the air flow in the intake pipe into the surrounding chamber and are directed onto the radially oriented bottom.
- This chamber floor acts as a reflector.
- German patent DE 743 418 A thus teaches intake noise damping by resonance coupling to a reflection damper.
- Attenuators of this type are only suitable for low frequencies, for example to attenuate Second-order motor pulsations only have a single defined resonance frequency per chamber, i.e. no frequency band, no matter how narrow, and also require a large installation space, both because of the structure of each individual reflector chamber and because of the large number of reflector chambers are necessary to achieve an at least massive broadband of the intake silencer.
- an exhaust damper for internal combustion engines which is also known as an intake silencer or projectile baffle damper, is known and is designed as a single-tube resonance damper.
- the bores defining the resonance wavelength in the exhaust pipe are surrounded by an outer jacket due to the excess pressure in the exhaust pipe. This jacket affects the damping behavior of the exhaust silencer.
- Another intake silencer is known from US 4,350,223 A.
- This intake muffler is inserted into a flexible line consisting of a corrugated hose, which connects an opening in the body of the motor vehicle which sucks in the ambient air to the intake port of the air filter.
- This intake silencer dampens the air noise that arises in the intake area within a narrow frequency band that extends on both sides of the resonance frequency of the resonator.
- the intake silencers of the prior art exemplified above have the overall disadvantage of only usably damping within a comparatively narrow frequency band.
- dampers stuffed with insulation material are only suitable for systems that have only moderate overpressure.
- Silencers damped with insulation materials are unusable for use in a charger intake line.
- European patent specification EP-242 797 B1 for diffusers and German published patent application DE 41 43 408 A1 for a side-branch resonator can be tuned by flaps and valves Damper systems known that are adjustable according to the engine speed.
- 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.
- the strong acoustic radiation of such turbochargers namely the typical "turbocharger whistle” in the frequency range of around 2 - 4 kHz, can be attributed to this.
- the charging processes even in the intake line result in clearly radiating broadband noises lying in the frequency band of 4 - 6 kHz, which are called "hissing".
- the invention is accordingly based on the object to provide a broadband airborne sound absorber that can certainly also be used elsewhere, but especially an intake silencer for an internal combustion engine which, with the smallest possible and flexibly adaptable structural volume, flexibly and effectively attenuates airborne noise over a wide frequency band in a flexible adaptation to the specific application requirements can
- an intake silencer should be able to dampen the noise generated in the motor vehicle internal combustion engine by turbochargers and radiated loudly in the frequency band of around 2-6 kHz in such a way that they are practically imperceptible both outside the vehicle and in the vehicle itself.
- an intake silencer of the type mentioned has the features mentioned in claim 1.
- an intake silencer achieves the greatest effect when it is switched into the intake duct in accordance with the features of claim 9, in particular the features of claim 10.
- the intake silencer according to the invention is accordingly constructed in such a way that the intake air flows through the damper, specifically in an intake pipe which is surrounded by a single, preferably two-layer resonator housing over the entire axial length on which the damping is effected.
- the intake pipe is provided in a manner known per se with openings which pass through the wall of the intake pipe open on both sides and connects the interior of the intake pipe with the interior of the resonator chambers formed in the resonator housing.
- the intake pipe In contrast to the prior art, there is the intake pipe however, not from a more or less thin steel sheet, but from materials such as aluminum, sintered metals, plastics or hard rubber, which enable the production of the intake pipe with larger wall thicknesses without making it unusably difficult.
- the wall thickness of the intake pipe is preferably in the range from 0.6 to 5 mm, in particular in the range from 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 is a question of the coordination between the cross-sectional area of the opening, the volume of the connected resonator chamber and the width and frequency position of the resonance absorption band to be set.
- the opening and the resonator chamber thus form a HELMHOLTZ resonator that is matched to the frequency band to be damped.
- the width of the active resonance absorption frequency band that can be set in this way increases with decreasing cross-sectional area of the opening. Since the efficiency of the coupling, ie the degree of damping that can be achieved, also decreases with decreasing cross-sectional area of the opening, the cross-sectional area of the opening must first be optimized between these two limit parameters.
- the annular space formed by the resonator housing around the perforated intake pipe is divided into a sequence in the axial direction of successive resonator chambers, each with a different volume, by chamber walls oriented transversely to the axial course of the intake pipe.
- These chamber walls are expediently molded onto the resonator housing itself and enclose an intake pipe designed as an insert.
- the suction pipe can also be firmly attached to it enclosing chamber walls and be introduced in this form as an insert in the resonator housing.
- the only decisive factor is that the resonator chambers formed in this way are hermetically delimited from one another.
- “Hermetically delimited from one another” means that the individual chambers are pneumatically and acoustically delimited from one another in such a way that the air volumes enclosed by them can be coupled in easily and can maintain stable resonance oscillation behavior undisturbed after swinging in, that is to say have a stable spring constant.
- each individual resonator chamber is ultimately only determined by the oscillating air volume with regard to its resonance frequency, and not by the fact that all camera walls are parallel to one another, the suction pipe runs centrally in the resonator housing or even the chamber walls are arranged parallel to one another.
- the intake silencer of the invention can be adapted to practically any available installation space with the smallest possible size.
- the damping resonance band assigned to this can be tuned primarily by dimensioning the chamber volume and by the wall thickness of the intake pipe wall in the region of the openings assigned to the respective chamber.
- the principle basically applies that the smaller the opening area, the wider the effective frequency band. As the opening area becomes smaller, however, the amount of damping also decreases, so that a compromise must be made between the required damping effect and the achievable broadband damping of each chamber.
- the adjacent chamber is then tuned such that the upper frequency of the absorption band, for example, overlap one chamber and the lower frequency of the absorption band of the adjacent chamber are sufficiently overlapping.
- the successive chambers so that their volumes decrease or increase steadily from one cell to the next. This is to mean that the resonator chamber volume of the chambers immediately following one another in the axial sequence increases steadily in a certain direction, continuously from the first to the last chamber, and accordingly decreases continuously in the opposite direction.
- the increase and decrease in chamber volumes from chamber to chamber are in principle 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 of the invention can in principle be made from any materials.
- the intake pipe and the resonator housing can also be made of the same material, since the resonator housing shell has practically no radiation. Also, no additional damping materials need to be used in order to prevent the noise from being emitted from the resonator housing.
- the intake silencer of the invention is preferably made of heat-resistant, preferably fiber-reinforced plastic, hard rubber or also of porous sintered materials or porous materials, especially of aluminum.
- the openings connecting the individual resonator chambers to the interior of the intake pipe can be both round, that is to say strictly cylindrical, and also oval, egg-shaped, slit-shaped and polygonal.
- all openings of the intake pipe are preferably formed with a circular cross section.
- the intake muffler When used in motor vehicles with superchargers, the intake muffler, which practically has no flow loss, is preferably switched directly into the intake line between the charger and the charge air cooler.
- the intake silencer of the invention is to be connected as close as possible to the pressure port of the supercharger, in particular to be flange-mounted directly to it or to be connected to it via the shortest possible acoustically insulating connection, or, preferably, to be integrated directly into the pressure port of the turbocharger, for example in the manner known from German patent DE 35 31 353 C2 for the intake manifold of an intercooler.
- Figure 1 shows an embodiment of the invention in perspective and with the cover of the resonator housing removed.
- 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 a two-shell resonator housing 4 enclosing this to form a closed annular space 2, only one of the two being shown in FIG. 1 for the sake of clarity housing shells that can be assembled to fit is shown.
- the intake silencer 1 is provided with an inlet port 5 and an outlet port 6 for switching on in the intake line Internal combustion engine equipped.
- the inlet connection 5 is shown as being formed in one piece with the intake pipe, while the outlet connection 6 is shown as being connected in one piece with the resonator housing shell shown. In principle, this type of design of the connecting piece is interchangeable.
- both connecting pieces i.e. both the inlet piece and the outlet piece
- both connecting pieces are formed in one piece with the resonator housing, and preferably in such a way that one of the two connecting pieces is formed on one of the two resonator housing shells, the other on the other housing shell or otherwise with this are trained.
- This has the effect that, in the case of a two-shell configuration of the intake pipe as an insert in the resonator housing, a closing pressure which serves to tighten and serves for sealing purposes can be exerted when the resonator housing is closed by welding, screwing or otherwise.
- Openings 7 are formed in the tube wall of the intake pipe 2, which connect the interior of the intake pipe 2 to the annular space 3 of the resonator housing 4. Each of these openings is circular in cross section, and has a diameter of 3 mm with a wall thickness of the intake pipe 2 in the opening area of 2 mm.
- resonator chambers 9 are formed in succession in the resonator in axial order each have a different volume from the other.
- the individual chamber volumes are determined not only by the spacing of the chamber partition walls 8 from one another, but also by the specific design of the resonator housing 4 itself.
- the openings 7 are arranged in the intake pipe 2 so that each of the resonator chambers 9 is connected to the interior of the intake pipe 2, with the formation of a small oscillatable air mass in the opening, in such a way that none of the camera walls thereby bridges, i.e. is short-circuited with one of the neighboring chambers.
- all openings 7 of the intake pipe 2 have the same geometric configuration and the same dimensions.
- both the distribution and the number of openings 7 provided in the intake pipe 2 per chamber 9 should be identical from chamber to chamber. In the manner shown schematically in FIG. 1, however, this will rarely be possible in practice, since the design and dimensions of the intake silencer have to be taken into account.
- the intake pipe is formed within the resonator housing 4 with an oval cross section, a channel-like region of the intake pipe 2 extending from the inlet connector 5 to the outlet connector 6 having no holes 7.
- This serves the purpose of not allowing moisture, for example atmospheric moisture or oil dust, to drip with the intake air when condensing in the intake pipe 2 into the resonator chambers 9 through the openings 7, but rather for this condensate to be discharged into the resonator housing from the outlet port 6 of the intake silencer 1 run out to 1 (it should be noted that in the illustration shown in FIG. 1, the spatial position of the muffler 1 does not correspond to its installation position. This is after rotating the intake muffler 1 shown in FIG. 1 by 90 ° clockwise around the longitudinal axis of the intake pipe 2 get around).
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
- Compressor (AREA)
Abstract
Description
Claims
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 (de) | 1996-04-22 | 1997-04-22 | Ansaugschalldämpfer und kraftfahrzeug |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0834011A1 true EP0834011A1 (de) | 1998-04-08 |
EP0834011B1 EP0834011B1 (de) | 2000-05-31 |
EP0834011B2 EP0834011B2 (de) | 2004-10-27 |
Family
ID=7792036
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97920737A Expired - Lifetime EP0834011B2 (de) | 1996-04-22 | 1997-04-22 | Ansaugschalldämpfer und kraftfahrzeug |
Country Status (5)
Country | Link |
---|---|
US (1) | US5979598A (de) |
EP (1) | EP0834011B2 (de) |
DE (2) | DE19615917A1 (de) |
ES (1) | ES2146465T5 (de) |
WO (1) | WO1997040271A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6802388B2 (en) | 2001-06-13 | 2004-10-12 | Woco Franz-Josef Wolf & Co. Gmbh | Silencer or noise damper |
Families Citing this family (88)
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DE19750102A1 (de) * | 1997-11-12 | 1999-06-02 | Stankiewicz Gmbh | Gasdurchströmte Leitung mit Schallabsorptionswirkung |
JP4010470B2 (ja) * | 1998-03-27 | 2007-11-21 | ヤマハ発動機株式会社 | 跨座式船艇の船体構造 |
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DE10243881A1 (de) * | 2002-09-21 | 2004-04-01 | Mann + Hummel Gmbh | Schalldämpfer zur Verringerung von Luftgeräuschen und Verfahren zur Herstellung desselben |
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DE10341319B4 (de) * | 2003-09-08 | 2006-02-02 | Veritas Ag | Schalldämpfer |
US20050150718A1 (en) * | 2004-01-09 | 2005-07-14 | Knight Jessie A. | Resonator with retention ribs |
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EP2161424A1 (de) | 2008-09-04 | 2010-03-10 | WOCO Industrietechnik GmbH | Fluidführungseinrichtung und Schalldämpfer sowie Abgasanlage mit solch einer Fluidführungseinrichtung |
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US8651800B2 (en) | 2010-06-04 | 2014-02-18 | Gm Global Technology Operations Llp | Induction system with air flow rotation and noise absorber for turbocharger applications |
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CN102996302B (zh) * | 2012-08-11 | 2016-01-27 | 郭荣 | 一种可同时消除宽频带和窄频带噪声的消声器 |
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JP6173820B2 (ja) * | 2013-08-01 | 2017-08-02 | 株式会社神戸製鋼所 | ガス圧縮機用の熱交換器 |
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CN104712470A (zh) * | 2013-12-13 | 2015-06-17 | 北汽福田汽车股份有限公司 | 用于确定空滤器进气管谐振腔结构的测试装置 |
WO2015092488A1 (en) | 2013-12-19 | 2015-06-25 | Teklas Kaucuk Sanayi Ve Ticaret A.S. | Modular sound absorber |
JP2015175297A (ja) * | 2014-03-14 | 2015-10-05 | トヨタ自動車株式会社 | 吸気ダクト |
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DE202014007986U1 (de) * | 2014-10-01 | 2016-01-05 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Schalldämpfer |
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US9376946B1 (en) * | 2015-04-02 | 2016-06-28 | Fisher Controls International Llc | Modal attenuator |
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CN105422337B (zh) * | 2015-12-07 | 2018-12-14 | 华中科技大学 | 一种进气消声器 |
CN106930873A (zh) * | 2015-12-30 | 2017-07-07 | 上海索菲玛汽车滤清器有限公司 | 具有消声结构的进气管 |
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CN108386253B (zh) * | 2018-03-28 | 2020-12-08 | 峡江县飞福科技有限公司 | 一种装载机消音机构 |
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1996
- 1996-04-22 DE DE19615917A patent/DE19615917A1/de not_active Withdrawn
-
1997
- 1997-04-22 US US08/983,024 patent/US5979598A/en not_active Expired - Lifetime
- 1997-04-22 DE DE59701802T patent/DE59701802D1/de not_active Expired - Lifetime
- 1997-04-22 ES ES97920737T patent/ES2146465T5/es not_active Expired - Lifetime
- 1997-04-22 EP EP97920737A patent/EP0834011B2/de not_active Expired - Lifetime
- 1997-04-22 WO PCT/EP1997/002038 patent/WO1997040271A1/de active IP Right Grant
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6802388B2 (en) | 2001-06-13 | 2004-10-12 | Woco Franz-Josef Wolf & Co. Gmbh | Silencer or noise damper |
Also Published As
Publication number | Publication date |
---|---|
EP0834011B1 (de) | 2000-05-31 |
US5979598A (en) | 1999-11-09 |
ES2146465T3 (es) | 2000-08-01 |
ES2146465T5 (es) | 2005-04-16 |
EP0834011B2 (de) | 2004-10-27 |
DE19615917A1 (de) | 1997-10-30 |
WO1997040271A1 (de) | 1997-10-30 |
DE59701802D1 (de) | 2000-07-06 |
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