• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Turbocharger, with a turbine for the expansion of a first medium and for generating energy during the expansion of the first medium, and with a compressor for compressing a second medium using the energy obtained in the turbine, at least one flow-guiding element of the turbocharger with a silencer (1), the respective silencer (1) having a support structure (3) with a support wall (4) and with chambers (5) formed on the support wall (4), the chambers (5) on one of a flow channel (7) of the silencer (1) facing away from the same are delimited by the supporting wall (4), and the chambers (5) on a side facing the flow channel (7) of the silencer (1) are delimited by a cover (8) wherein the cover (8) has at least two grid-shaped layers (9, 10, 11) firmly connected to one another with different mesh sizes.
    公开号:CH712704B1
    申请号:CH00502/17
    申请日:2017-04-12
    公开日:2021-03-31
    发明作者:Hermann Ricardo；Büssow Richard
    申请人:Man Energy Solutions Se；
    IPC主号:
    专利说明:

    The invention relates to a turbocharger.
    From DE 198 18 873 C2 a reciprocating internal combustion engine with at least one exhaust gas turbocharger is known. At least one flow-guiding element of the exhaust gas turbocharger is assigned a silencer based on the principle of a Helmholtz resonator. The respective muffler has a support structure made up of an outer support wall and a plurality of chambers received by the support wall, the chambers being delimited by a perforated plate on a side of the muffler facing a flow channel.
    The known from the prior art use of silencers, which are based on the principle of a Helmholtz resonator, has the disadvantage that in principle only a very limited frequency range can be effectively soundproofed. If the frequency is outside this frequency range, the damping effect is greatly reduced.
    Based on this, the present invention is based on the object of creating a new type of turbocharger with improved sound absorption.
    This object is achieved by a turbocharger according to claim 1. According to the invention, the cover has at least two grid-like layers firmly connected to one another with different mesh sizes.
    In the exhaust gas turbocharger according to the invention, the cover of the respective muffler is designed in several layers, the cover having at least two firmly interconnected, grid-shaped layers with different mesh sizes. This makes it possible to provide a silencer with an improved silencing effect. In particular, the silencer with such a cover has a better damping effect over a broader frequency range.
    According to an advantageous development of the invention, the lattice-shaped layers of the cover are formed with different mesh sizes of wire mesh, the wire mesh of the individual layers not only having different mesh sizes but also different wire diameters. This makes it possible to provide a particularly advantageous sound-damping effect.
    The cover preferably has a thickness t, the chambers having a depth a defined by the distance between the cover and the supporting wall, t being smaller than a. This serves to provide a particularly advantageous soundproofing effect.
    In particular, a ratio t / a between the thickness t of the cover and the depth a of the chambers is between 0.2 and 0.025. These details also serve to provide a particularly advantageous soundproofing effect.
    According to an advantageous development, a ratio a / A between the depth a of the chambers and a sound wavelength λ of the frequency to be attenuated is between 0.25 and 0.4. In this way, the soundproofing effect can be further improved.
    According to an advantageous development, the respective muffler is integrated into the respective flow-guiding element of the turbocharger, preferably in a spiral-like discharge housing of the compressor. The integration of the muffler in a spiral-like discharge housing of the compressor is particularly preferred, since this allows a particularly good sound-damping effect to be provided with minimal space requirements.
    According to an advantageous development, the chambers of the support structure have alternately different widths, viewed in the direction of flow through a flow channel of the muffler. In this way, the sound-damping effect can be further improved.
    [0013] Further developments of the invention emerge from the dependent claims and the following description. Exemplary embodiments of the invention are explained in more detail with reference to the drawing, without being restricted thereto. 1 shows a schematic cross section through a silencer of a turbocharger according to the invention; FIG. 2: the detail II of FIG. 1 in a perspective view.
    The present invention relates to a turbocharger. The person skilled in the art addressed here is familiar with the basic structure of a turbocharger. A turbocharger has a turbine for the expansion of a first medium, in particular for the expansion of exhaust gas, with energy being obtained in the process. Furthermore, a turbocharger comprises a compressor for compressing a second medium, in particular for compressing charge air, with energy being used in the compressor that was obtained during the expansion of the first medium in the turbine.
    A turbocharger has different flow-guiding assemblies. This includes, in particular, a so-called discharge housing of the compressor of the exhaust gas turbocharger. At least one flow-guiding element of the turbocharger is provided with a silencer 1.
    Fig. 1 shows a schematic cross section through a muffler 1, which interacts with a flow-guiding element of the turbocharger, for example with the spiral-shaped discharge housing of the compressor of the turbocharger.
    In FIG. 1, the muffler 1 has flanges 2 via which the muffler 1 can be screwed to other flow-guiding assemblies of the turbocharger. The silencer 1 shown in FIG. 1 is accordingly a separate assembly of the turbocharger, which is screwed to other assemblies of the same.
    The muffler 1 has a support structure 3 with a support wall 4 and with chambers 5 formed on the support wall 4. The support wall 4 is in particular a radially outer tube. On this radially outer tube, which provides the support wall 4, chambers 5 are formed, which are formed or delimited from one another by metal sheets 6 which extend essentially in the radial direction of the support wall 4.
    A flow channel 7 of the muffler 1 adjoins the chambers 5 of the support structure 3 radially on the inside, through which a sound-damping medium flows.
    As already mentioned, the chambers 5 are delimited by the supporting wall 4 on a side facing away from the flow channel 7. On a side facing the flow channel 7, the chambers 5 of the support structure 3 are delimited by a cover 8.
    The cover 8 has at least two firmly interconnected, grid-shaped layers with different mesh sizes. In Fig. 1 and 2, a cover 3 is shown from three firmly interconnected, grid-shaped layers 9, 10 and 11, each of which has different mesh sizes.
    Particularly preferably, the grid-shaped layers 9, 10 and 11 of the cover 8, which have the different mesh sizes, each provided by a wire mesh, this wire mesh of the individual layers 9, 10 and 11 preferably not only different mesh sizes but also different wire diameters exhibit.
    1 it can be seen that the chambers 5 of the support structure 3 have a depth a in the radial direction which is defined by the distance between the cover 8 and the support wall 4. According to FIG. 2, the cover 8 has a radial thickness t. The thickness t of the cover 8 is smaller than the depth a of the chambers 5.
    A ratio t / a between the thickness t of the cover 8 and the depth a of the chambers 5 is preferably between 0.2 and 0.025.
    Viewed in the direction of flow through the flow channel 7 of the muffler 1, the chambers 5 of the support structure 3 have a width b, wherein in FIG. 1 the chambers 5 of the support structure 3 each alternately have different widths b in the flow direction of the flow channel 7.
    According to a particularly preferred embodiment, a ratio a / λ between the depth a of the chambers 5 of the support structure 3 and a sound wavelength λ of the frequency to be damped is between 0.25 and 0.4.
    In this case, a ratio RS / Z0 between the acoustic specific flow resistance RS and the characteristic acoustic impedance Z0 of the medium to be damped with regard to its sound noise is between 0.25 and 4. The acoustic specific flow resistance RS is between 350 and 5500 Pa * s / m in turbocharger compressors .
    The depth a of the chambers 5 of the support structure 3 is particularly preferably between 15 mm and 90 mm.
    In the embodiment of FIG. 1, the muffler 1 is designed as a separate assembly and connected via the flanges 2 to another flow-guiding element of the turbocharger.
    In contrast to this, it is also possible to integrate the muffler 1 in a flow-guiding element of the turbocharger, particularly preferably in a flow-guiding, spiral-like discharge housing of the compressor of the turbocharger.
    The muffler 1 acts like a λ / 4 resonator and has a good soundproofing effect over a wide frequency range.
    List of reference symbols
    1 silencer 2 flange 3 supporting structure 4 supporting wall 5 chamber 6 sheet metal 7 flow channel 8 cover 9 layer 10 layer 11 layer
    权利要求:
    Claims (10)
    [1]
    1. Turbocharger, with a turbine for expanding a first medium and for generating energy during the expansion of the first medium, and with a compressor for compressing a second medium using the energy obtained in the turbine, with at least one flow-guiding element of the turbocharger with a muffler (1) is provided, the respective muffler (1) having a support structure (3) with a support wall (4) and with chambers (5) formed on the support wall (4), the chambers (5) on one of a flow channel of the silencer facing away from the same are delimited by the support wall (4), and wherein the chambers (5) on a side facing the flow channel (7) of the silencer are limited by a cover (8), characterized in that the cover (8) has at least two grid-shaped layers (9, 10, 11) firmly connected to one another with different mesh sizes.
    [2]
    2. Turbocharger according to claim 1, characterized in that the grid-shaped layers (9, 10, 11) of the cover (8) have different wire diameters.
    [3]
    3. Turbocharger according to claim 1 or 2, characterized in that the cover (8) has a thickness t, that the chambers (5) have a depth a defined by the distance between the cover (8) and the supporting wall (4), wherein t is less than a.
    [4]
    4. Turbocharger according to claim 3, characterized in that a ratio t / a between the thickness t of the cover (8) and the depth a of the chambers (5) is between 0.2 and 0.025.
    [5]
    5. Turbocharger according to claim 3 or 4, characterized in that a ratio a / λ between the depth a of the chambers (5) and a sound wavelength λ of the frequency to be damped is between 0.25 and 0.4.
    [6]
    6. Turbocharger according to one of claims 3 to 5, characterized in that the depth a of the chambers (5) of the supporting structure (3) is between 15 mm and 90 mm.
    [7]
    7. Turbocharger according to one of claims 1 to 6, characterized in that the respective silencer (1) is integrated into the respective flow-guiding element of the turbocharger.
    [8]
    8. Turbocharger according to claim 7, characterized in that the respective silencer (1) is integrated into a spiral-like discharge housing of the compressor of the turbocharger.
    [9]
    9. Turbocharger according to one of claims 1 to 6, characterized in that the respective silencer (1) is designed as a separate assembly and is connected to the respective flow-guiding element of the turbocharger.
    [10]
    10. Turbocharger according to one of claims 1 to 9, characterized in that the chambers (5) of the supporting structure (3) have alternately different widths b viewed in the flow direction of a flow channel (7) of the silencer (1).
    类似技术:
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    DE3934756C2|1992-03-05|
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    同族专利:
    公开号 | 公开日
    CH712704A2|2018-01-15|
    DE102016112333A1|2018-01-11|
    JP2018003845A|2018-01-11|
    KR20180005594A|2018-01-16|
    CN107587959B|2021-05-28|
    CN107587959A|2018-01-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4294329A|1979-12-17|1981-10-13|Rohr Industries, Inc.|Double layer attenuation panel with two layers of linear type material|
    US4421455A|1981-12-22|1983-12-20|The Garrett Corporation|Duct lining|
    GB8817669D0|1988-07-25|1988-09-01|Short Brothers Ltd|Means for attenuating sound energy|
    DE19818873C2|1998-04-28|2001-07-05|Man B & W Diesel Ag|Reciprocating internal combustion engine|
    GB9909581D0|1999-04-26|1999-06-23|Short Brothers Plc|Noise attenuation panel|
    DE10345575C5|2003-09-29|2011-08-11|Härle, Hans A., 73441|Device for acoustic and thermal shielding|
    EP1602810A1|2004-06-04|2005-12-07|ABB Turbo Systems AG|Sound absorber for compressor|
    DE102011005025A1|2011-03-03|2012-09-06|Siemens Aktiengesellschaft|Resonator silencer for a radial flow machine, in particular for a centrifugal compressor|DE102017118803A1|2017-08-17|2019-02-21|Volkswagen Aktiengesellschaft|Fluid pipe for an internal combustion engine, internal combustion engine with a fluid pipe and method for producing a fluid pipe|
    US10780940B2|2018-01-12|2020-09-22|Shimano Inc.|Human-powered vehicle control device|
    DE102018102237A1|2018-02-01|2019-08-01|Man Energy Solutions Se|Silencer and compressor|
    法律状态:
    2018-07-31| PFA| Name/firm changed|Owner name: MAN ENERGY SOLUTIONS SE, DE Free format text: FORMER OWNER: MAN DIESEL AND TURBO SE, DE |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102016112333.1A|DE102016112333A1|2016-07-06|2016-07-06|turbocharger|
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