EP3692264B1 - Atténuateur sonore pouvant être relié à une partie de compresseur d'un turbocompresseur - Google Patents

Atténuateur sonore pouvant être relié à une partie de compresseur d'un turbocompresseur Download PDF

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Publication number
EP3692264B1
EP3692264B1 EP17780713.8A EP17780713A EP3692264B1 EP 3692264 B1 EP3692264 B1 EP 3692264B1 EP 17780713 A EP17780713 A EP 17780713A EP 3692264 B1 EP3692264 B1 EP 3692264B1
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EP
European Patent Office
Prior art keywords
micro
perforated plate
air
silencer
diameter
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.)
Active
Application number
EP17780713.8A
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German (de)
English (en)
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EP3692264A1 (fr
Inventor
Aleksi KYTÖLÄ
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.)
Wartsila Finland Oy
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Wartsila Finland Oy
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Publication of EP3692264A1 publication Critical patent/EP3692264A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference

Definitions

  • the present invention relates to an air silencer connectable to a compressor part of a turbocharger according to the preamble of claim 1.
  • a compressor wheel of a turbocharger is a significant source for highfrequency engine room noise which is commonly attenuated with an air filter silencer attached to the suction side of the turbocharger. Noise attenuating wool based silencers is commonly used for reducing the noise.
  • US6736238B2 discloses an air intake silencer which comprises a casing supporting an axially spaced array of three annular noise attenuating baffles each of which defines a central circular aperture centered on the axis of the casing.
  • Each of the baffles are axially separated from each other and from an end cap and end flange, the baffles defining inlet flow passages.
  • Each of the baffles, the end cap, and the end flange have the same general construction comprising a layer of acoustic material sandwiched between a pair of perforated steel support flanges shaped appropriately.
  • the manner of attaching the silencer to the turbocharger causes the turbocharger to bear all the weight from the silencer, which can cause problems if the whole package starts to vibrate due to engine vibrations and passing flow.
  • a large and heavy silencer can increase the vibrations to the turbocharger which in turn might lead to damaging the turbine or compressor wheels that have a very small clearance to the casing.
  • Document US 5 140 819 A discloses an air silencer connectable to a compressor part of a turbocharger comprising a flange part provided with an air passage configured to be connectable with an air intake opening of the compressor part in an air tight manner, a number of noise attenuating baffles being separated from each other so as to form air passage for an inlet air through the air silencer to the air passage, wherein the baffles comprise a micro-perforated plate provided with a micro-perforation, and a back plate, and a space arranged between the micro-perforated plate and the back plate, and the space comprises a spacer matrix providing a number of sub-cavities in the space fluidly communicating with the micro-perforation.
  • An object of the invention is to provide a smaller and more lightweight noise silencer which still accomplishes desired noise attenuation and pressure loss level.
  • a silencer according to claim 1 is provided.
  • the air silencer is configured to attenuate a selected frequency and the effective diameter is less than half of the wave length of the selected attenuation frequency.
  • the first and the second spaces are separated from each other by a common back plate arranged between the first micro-perforated plate and the second micro-perforated plate.
  • the spacer matrix extends evenly over the area between the back plate and the micro-perforated plate.
  • the sub cavities of the spacer matrix are fluidly separated from each other.
  • the spacer matrix comprises a honey-comb structure provided with wall extending perpendicular to the plane of the micro-perforated plate.
  • the micro-perforated plate comprises circular openings having their diameter ⁇ 1 mm.
  • the micro-perforated plate comprises circular openings having equal diameters, and that a distance between centers of two adjacent openings to the diameter of the opening is less than 0,2.
  • the micro-perforated plate com-prises circular openings having equal diameters and equal distance between the openings, and that the ratio of a distance between centers of two adjacent openings to the diameter of the opening is less than 0,2.
  • thickness of the micro-perforated plate is 0,5 - 2 times the diameter of the circular opening.
  • the depth of the space is 2 - 25 times the diameter of the circular opening.
  • the flange part provided with central air passage and the noise attenuating baffles are of circular shape provided with central opening coaxial with the flange part, and that the silencer comprises an end cover arranged parallel with and at a distance from the flange part and that the noise attenuating baffles are stacked between the flange part and the end cover.
  • the noise attenuating baffle is of circular shape provided with central opening coaxial with the flange part, and that radially inner and outer rims of the baffle are gas tightly sealed.
  • This provides air silencer for a turbocharger the performance of which is considerably improved.
  • the invention provides significantly wider attenuating bandwidth compared to traditional turbocharger silencers.
  • FIG. 1 depicts schematically a turbocharger 10 which may be installed in an internal combustion piston engine. There is also shown an enlarged view W of a section relating to an air silencer 24.
  • the turbocharger unit 10 comprises a compressor part 12 and a turbine part 18.
  • the compressor part has an air inlet 14 and an air outlet 16, and the turbine part 18 has an exhaust gas inlet 20 and an exhaust gas outlet 22.
  • the turbine part (turbine wheel, not shown) and the compressor part (compressor wheel, not shown) are mechanically connected by a shaft (not shown) so that the turbine wheel is arranged to rotate the compressor wheel.
  • the turbocharger unit is provided with an inlet air silencer 24 through which the air to be compressed in the compressor part is arranged to flow as depicted by the arrows A.
  • silencer means a device which is to at least some extent capable of removing impurities from the gas and additionally or alternatively attenuate noise emitted from the compressor part.
  • the air silencer 24 comprises a flange part 26 at its one axial end and an end cover 28 at the opposite axial end, which are arranged parallel at a distance from each other. Between the flange part 26 and the end cover 28 there is arranged an air permeable filter element 30.
  • the filter element 30 is of cylindrical shape and annularly arranged to circumscribe the rim area between the flange part and the end cover and having an axial length equals to the distance between the flange part 26 and the end cover 28.
  • the flange part 26 comprises attaching means for attaching the air silencer 24 in connection with the air inlet of the compressor part 12.
  • the flange part 26 is provided with a central air passage 32 so that the air, which has flown through the filter element 30 into the air silencer 24, may flow through the air passage 32 to the compressor part 12.
  • FIG. 1 depicts schematically a structure of an air silencer 24 according to an embodiment of the invention.
  • the air silencer comprises a number of baffles 50 arranged one of the other in the axial direction D which correspond the direction of the axis of the turbocharger.
  • the baffles 50 are fixed to the air silencer by means of suitably threaded bars 52, such a stud bolts, which a fixed to the flange part 26.
  • the baffles 50 are arranged such that there is an axial distance between the baffles 50 which form air passages 54 between the baffles 50.
  • the baffles 50 are spaced so that there is a bushing 51 arranged to the bars 52 between each baffle 50, the axial length of which defines the width of the air passage 54.
  • the package of the baffles and the bushings is tightened by the end cover 28 using the threaded bars 52.
  • FIG. 2 depicts schematically a structure of a two-sided baffle 50 according to an embodiment of the invention showing the successive layers of the baffle 50 as cut-outs inside each other.
  • the baffle 50 is advantageously made of metal.
  • the baffle comprises a first micro-perforated plate 56.1, provided with a micro-perforation 53, on a face of the baffle 50 along the surface of which the air is arranged to flow in the air silencer.
  • the micro-perforation advantageously consists of substantially circular openings.
  • the micro-perforation is shown in exaggerated manner by small crosses for illustrative reasons.
  • the next layer in the baffle 50 comprises a space 57 under the first micro-perforated plate 56.1.
  • the space 57 is closed i.e. sealed in gas tight manner, at the radial edges 50.1, 50.2 of the baffle 50.
  • the spacer matrix 58 comprises multiple walls 62 extending between the micro-perforated plate 56.1 and back plate 60 so as to form a number of sub cavities 64 into the space 57.
  • On the right side of the baffle 50 in the figure 2 the first spacer matrix 58.1 is presented visible below the first micro-perforated plate 56.1. This demonstrates that the cross sectional area of each sub cavity 64 is such that more than one opening in the micro-perforation 64 opens into one sub cavity 64.
  • the spacer matrix 58 extends over the area of the space.
  • the next layer in the baffle, being behind the back plate in the figure 2 is the space 57 and after that a second micro-perforated plate 56.2, provided with a micro-perforation. Respectively there is a second spacer matrix 58.2 arranged into the space 57.
  • the second spacer matrix 58.2 comprises multiple walls 62 extending between the second micro-perforated plate 56.2 and the back plate 60 so as to form a number of sub cavities 64 into the space 57.
  • the second spacer matrix 58.2 extends advantageously over the area of the space.
  • the baffle 50 comprises the first micro-perforated plate 56.1 and the second micro-perforated plate 56.2 and between them the space 57 partially bordered by the first micro-perforated plate, as well as the second space partially bordered by the second micro-perforated plate 58.2, in which the spaces 57 are separated from each other by the common back plate 60.
  • the space and the sub cavity are empty, i.e. filled only with the air.
  • the sub cavities 64 are fluidly separated from each other. This way the adjacent sub cavities are not effected by each other and the air space in the sub cavity acts as locally reacting space, meaning that each one of the hole acts like an independent attenuator.
  • the first micro-perforated plate 56.1, the first spacer matrix 58.1 and the back plate 60 form a first noise attenuator and the second micro-perforated plate 56.2, the second spacer matrix 58.2 and the back plate 60 form a second noise attenuator.
  • the first and the second attenuators are configured to attenuate noise at different frequency. In practise this means that the air silencer can be effective over wider frequency range.
  • the spacer matrix 58 in both of the noise attenuators comprises a honeycomb structure provided with wall extending perpendicular to the plane of the micro-perforated plate 56.
  • Figure 3 shows a partial cross section view III-III of the figure 2 illustrating the structure of the baffle 50 shown in the figure 2 .
  • the effective diameter is less than half of the wave length of the selected attenuation frequency.
  • the air silencer is dimensioned according to the selected attenuation frequency which usually is the dominant frequency of the noise.
  • the invention provides very effective silencer particularly for attenuating noise at the BPF.
  • the structure of the spacer matrix may be other than a honeycomb as long as the spacer matrix forms sub cavities which fulfils the condition set the effective diameter above.
  • the micro-perforated plate comprises circular openings having their diameter ⁇ 1 mm.
  • the only one sided baffle comprising only the first noise attenuator, may be used.
  • the baffle 50 is comprised of a plate with small holes with a diameter less than 1 mm.
  • the hole operationally attached to a locally reacting sub cavity behind the holes. Attenuation is based on friction losses that occur when the air passes through the small holes and resonance that occurs caused by the sub cavity.
  • the attenuated frequency range is significantly wider compared to a traditional resonator.
  • Attenuation bandwidth and intensity can be adjusted by changing diameter of the holes, depth of the sub cavity cooperating with the holes, thickness of the perforated plate, and perforation constant, i.e. area of the holes in respect to the area of the plate.
  • the friction losses occur as the sound waves move through the small holes.
  • the amount of the losses depend on the parameters of the micro-perforated plate and the properties of the fluid (air).
  • the holes (and the perforation constant) need to be small enough so that they restrict the sound waves to propagate through them. Reactance causes the sound waves to resonate through the hole when the sound waves pass through the hole many times, the friction losses caused by the hole are also added many times.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Claims (13)

  1. Atténuateur sonore (24) pouvant être raccordé à une partie de compresseur (12) d'un turbocompresseur (10) comprenant une partie de bride (26) pourvue d'un passage d'air (54) configurée afin d'être raccordée à une ouverture d'admission d'air de la partie de compresseur de manière étanche à l'air,
    un certain nombre de déflecteurs d'atténuation de bruit (50) étant séparés les uns des autres de manière à former un passage d'air (54) pour un air d'admission à travers l'atténuateur sonore (24) vers le passage d'air (54), dans lequel les déflecteurs (50) comprennent une plaque micro-perforée (56,1 ,56,2) munie d'une micro-perforation (53), et une plaque arrière (60), et un espace (57) agencé entre le plaque micro-perforée (56.1, 56.2) et la plaque arrière (60), et l'espace (57) comprend une matrice d'espacement (58.1, 58.2) fournissant un certain nombre de sous-cavités (64) dans l'espace (57) communiquant fluidiquement avec la micro-perforation (53), caractérisé en ce qu'au moins un des déflecteurs (50) dans l'atténuateur sonore (24) comprend une première plaque micro-perforée (56,1 ,56,2) et une deuxième plaque micro-perforée (56,1 ,56,2) et entre celles-ci un premier espace (57) partiellement bordé par la première plaque micro-perforée (56,1 , 56,2), et un deuxième espace (57) partiellement bordé par la deuxième plaque micro-perforée (56,1 ,56,2), dans lequel le premier et le deuxième espace (57) sont séparés fluidiquement l'un de l'autre, et que la première plaque micro-perforée (56.1, 56.2) comprend des ouvertures ayant un premier diamètre et la deuxième plaque micro-perforée (56.1, 56.2) comprend des ouvertures ayant un deuxième diamètre, différent du premier diamètre.
  2. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la sous cavité (64) a un diamètre effectif De = (4 A)/P, dans lequel A est la section transversale et P est la longueur du périmètre de la sous-cavité (64) et que le diamètre effectif est inférieur à la moitié de la longueur d'onde de la fréquence d'atténuation sélectionnée.
  3. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que le premier et le deuxième espaces sont séparés l'un de l'autre par une plaque arrière commune (60) disposée entre la première plaque micro-perforée (56,1, 56,2) et la deuxième plaque micro-perforée (56,1, 56,2).
  4. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la matrice d'espacement (58.1, 58.2) s'étend uniformément sur la zone comprise entre la plaque arrière (60) et la plaque micro-perforée (56.1, 56.2).
  5. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que les sous-cavités (64) de la matrice d'espacement (58.1, 58.2) sont séparées fluidiquement les uns des autres.
  6. Atténuateur sonore (24) selon la revendication 1 ou 5, caractérisé en ce que la matrice d'espacement (58.1, 58.2) comprend une structure en nid d'abeille munie de parois s'étendant perpendiculairement au plan de la plaque micro-perforée (56.1, 56.2).
  7. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la plaque micro-perforée (56.1, 56.2) comporte des ouvertures circulaires, le diamètre des ouvertures circulaires est < 1 mm.
  8. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la plaque micro-perforée (56.1, 56.2) comporte des ouvertures circulaires ayant des diamètres égaux, et qu'une distance entre les centres de deux ouvertures adjacentes au diamètre de l'ouverture est inférieure à 0,2.
  9. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la plaque micro-perforée (56.1, 56.2) comprend des ouvertures circulaires ayant des diamètres égaux et une distance égale entre les ouvertures, et que le rapport d'une distance entre les centres de deux ouvertures adjacentes sur le diamètre de l'ouverture est inférieur à 0,2.
  10. Atténuateur sonore (24) selon la revendication 1 ou 8, caractérisé en ce que l'épaisseur de la plaque micro-perforée (56.1, 56.2) est de 0,5 à 2 fois le diamètre de l'ouverture circulaire.
  11. Atténuateur sonore (24) selon la revendication 1 ou 8, caractérisé en ce que la profondeur de l'espace (57) est de 2 à 25 fois le diamètre de l'ouverture circulaire.
  12. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que la partie de bride (26) munie d'un passage d'air central (54) et les déflecteurs d'atténuation de bruit (50) sont de forme circulaire pourvue d'une ouverture centrale coaxiale à la partie de bride (26), et que l'atténuateur sonore (24) comporte un couvercle d'extrémité disposé parallèlement et à distance de la partie de bride (26) et que les déflecteurs d'atténuation de bruit (50) sont empilés entre la partie de bride (26) et le couvercle d'extrémité.
  13. Atténuateur sonore (24) selon la revendication 1, caractérisé en ce que le déflecteur d'atténuation de bruit est de forme circulaire pourvu d'une ouverture centrale coaxiale à la partie de bride (26), et que les rebords radialement intérieur et extérieur du déflecteur sont scellés de manière étanche aux gaz.
EP17780713.8A 2017-10-04 2017-10-04 Atténuateur sonore pouvant être relié à une partie de compresseur d'un turbocompresseur Active EP3692264B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2017/075232 WO2019068323A1 (fr) 2017-10-04 2017-10-04 Atténuateur sonore pouvant être relié à une partie de compresseur d'un turbocompresseur

Publications (2)

Publication Number Publication Date
EP3692264A1 EP3692264A1 (fr) 2020-08-12
EP3692264B1 true EP3692264B1 (fr) 2021-12-01

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EP17780713.8A Active EP3692264B1 (fr) 2017-10-04 2017-10-04 Atténuateur sonore pouvant être relié à une partie de compresseur d'un turbocompresseur

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EP (1) EP3692264B1 (fr)
WO (1) WO2019068323A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110159600A (zh) * 2019-06-03 2019-08-23 宁波丰沃涡轮增压系统有限公司 一种集成有阻性消音器的增压器压壳结构
WO2022203508A1 (fr) * 2021-03-23 2022-09-29 Technische Universiteit Eindhoven Terminaison anéchoïque pour suppression d'onde de plan acoustique

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4294329A (en) * 1979-12-17 1981-10-13 Rohr Industries, Inc. Double layer attenuation panel with two layers of linear type material

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4421455A (en) * 1981-12-22 1983-12-20 The Garrett Corporation Duct lining
US5140819A (en) * 1989-09-28 1992-08-25 Sundstrand Corporation Turbine inlet silencer
GB0010895D0 (en) * 2000-05-05 2000-06-28 Nelson Burgess Ltd Air intake silencer
KR20010008001A (ko) * 2000-11-02 2001-02-05 권문구 원심형 냉매 압축기의 소음 소산 장치
DE102010028763B4 (de) * 2010-05-07 2015-04-02 Man Diesel & Turbo Se Schalldämpfer für einen Turboverdichter und Verfahren zum Auslegen eines Schalldämpfers

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4294329A (en) * 1979-12-17 1981-10-13 Rohr Industries, Inc. Double layer attenuation panel with two layers of linear type material

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WO2019068323A1 (fr) 2019-04-11

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