EP1628004A1 - Schalldämpfer, Durchschnittbauelement und Herstellungsverfahren einer Kulisse - Google Patents

Schalldämpfer, Durchschnittbauelement und Herstellungsverfahren einer Kulisse Download PDF

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Publication number
EP1628004A1
EP1628004A1 EP05107559A EP05107559A EP1628004A1 EP 1628004 A1 EP1628004 A1 EP 1628004A1 EP 05107559 A EP05107559 A EP 05107559A EP 05107559 A EP05107559 A EP 05107559A EP 1628004 A1 EP1628004 A1 EP 1628004A1
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EP
European Patent Office
Prior art keywords
sectional
sound damper
splitter
damper according
sound
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
Application number
EP05107559A
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English (en)
French (fr)
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EP1628004B1 (de
Inventor
Willem Martin Pranger
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.)
Aarding Thermal Acoustics BV
Original Assignee
Aarding Thermal Acoustics BV
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 Aarding Thermal Acoustics BV filed Critical Aarding Thermal Acoustics BV
Publication of EP1628004A1 publication Critical patent/EP1628004A1/de
Application granted granted Critical
Publication of EP1628004B1 publication Critical patent/EP1628004B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/04—Silencing apparatus characterised by method of silencing by using resonance having sound-absorbing materials in resonance chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/30—Exhaust heads, chambers, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/10—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling in combination with sound-absorbing materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/24—Silencing apparatus characterised by method of silencing by using sound-absorbing materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J13/00—Fittings for chimneys or flues 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2900/00—Special arrangements for conducting or purifying combustion fumes; Treatment of fumes or ashes
    • F23J2900/13003—Means for reducing the noise in smoke conducing ducts or systems

Definitions

  • the invention relates to a sound damper for an exhaust, comprising at least one splitter, in which a sound-damping material, such as mineral wool, is accommodated, wherein the splitter comprises several sectional components, the splitter being at least partially provided with perforations for the transmission of sound.
  • a sound damper for an exhaust comprising at least one splitter, in which a sound-damping material, such as mineral wool, is accommodated, wherein the splitter comprises several sectional components, the splitter being at least partially provided with perforations for the transmission of sound.
  • Such a sound damper for an exhaust is known.
  • This sound damper is used, for example, in a gas turbine.
  • a gas turbine comprises and inlet, a compressor, a combustion chamber, a turbine and an exhaust.
  • the compressor increases the pressure of air fed from the inlet, which then flows into the combustion chamber.
  • this compressed air mixes with an injected fuel, such as gas.
  • the mixture ignites so that combustion takes place.
  • As a result expansion occurs which makes a turbine rotate.
  • the rotating turbine produces power.
  • the turbine is linked by a shaft to the compressor, that is to say some of the generated power is used to drive the compressor.
  • Downstream of the turbine an exhaust is provided, which in a power station opens into a chimney.
  • the air that flows from the turbine into the exhaust can still have speeds of 50 - 70 m/s.
  • a gas turbine creates an enormous noise, which has to be damped by a sound damper.
  • the known sound damper comprises several splitters (German: Kulissen) which are arranged in the longitudinal direction of the exhaust. The air flows essentially parallel to the sound-damping splitters.
  • Each splitter is made up of a framework of U-shaped sectional components that are joined to one another and run in the longitudinal direction and height direction of the splitter.
  • the framework provides the splitter with the necessary strength.
  • Mineral wool is accommodated in the compartments of the framework, that is to say between the U-shaped sectional components, to damp sound.
  • the side walls of the framework are covered by perforated sheets, which are welded to the framework.
  • the perforated sheets form a side wall permeable to sound, that is to say the sound can penetrate through the perforations into the sound-damping wool within the framework.
  • these sheets prevent the sound-damping wool being sucked out of the compartments of the framework by the air flowing past.
  • the temperature of the air that enters the exhaust is approximately 250 °C when the gas turbine is idling.
  • the temperature of said incoming air rises to 600 °C or more within a short timeframe.
  • the framework and the perforated sheets are usually made of stainless steel. Moreover, the dimensions of a gas turbine for a power station are large - the exhaust has, for example, a length of 10 metres.
  • a temperature gradient is also produced between the front and the back of the splitter. This gives rise to local expansion and therefore severe thermal stressing of the splitter, which can lead to fracture or cracking.
  • the weld by means of which the perforated sheets are fixed to the framework can also rupture, as a result of which the sound-damping wool disappears out of the framework.
  • the object of the invention is to provide a sound damper where the temperature resistance is improved.
  • sectional components are stacked on top of one another and the perforations are made in said sectional components.
  • the splitter is made up of sectional components which bear directly on one another. Furthermore, the sectional components are provided with the perforations at the location of the side walls of the splitter.
  • the functions of the provision of the requisite strength and rigidity and the transmission of sound are thus integrated in a single component, i.e. the sectional components stacked on top of one another. Therefore there is no separate framework - the known U-shaped sectional components in the longitudinal direction and in the height direction that make up the framework have been replaced by the sectional components stacked on top of one another.
  • the sound-damping splitter according to the invention is able to give if stresses arise as a consequence of temperature differences, local expansion not leading to cracking. As a result the splitter is better able to withstand thermal stresses.
  • a further advantage is that the splitter according to the invention is less expensive.
  • the splitter has fewer components, so that the construction time is reduced. In addition a saving in material is achieved.
  • the invention is particularly suitable for an exhaust for a gas turbine, the invention is not restricted to this.
  • the sound damper according to the invention can be used for any exhaust system, for example also the exhaust of a diesel engine.
  • the sectional components each have a first stacking end and a second stacking end, wherein said stacking ends have shaped parts engaging in one another for engaging the first stacking end of a first sectional component in the second stacking end of a second sectional component that is stacked adjacent to the first sectional component.
  • the stacking ends are, for example, formed by a bottom side and a top side of a sectional component, respectively.
  • the bottom side and top side then have shapes such that the top side of a lower sectional component and the bottom side of an adjacent upper sectional component, which is stacked in the height direction on the lower sectional component, engage in one another.
  • the sectional components stacked on top of one another are sideways confined with respect to one another. If a weld by means of which sectional components are welded to one another fails, the stacked sectional components will not immediately separate from one another. After all, the sectional components are already linked to one another with some degree of interlocking due to corresponding shapes.
  • the sectional components are provided with a base that has slanted side edges on either side thereof, wherein the base is joined at the slanted side edges to two respective upright side walls, which each have a slanted top edge at the end facing away from the base, wherein the slanted top edges are oriented towards one another.
  • the bottom side of the upper sectional component is formed by the base and the top side of the underlying sectional component is formed by the top edges.
  • the base is at least partially accommodated between the top edges.
  • the slanted edges of the sectional components reinforce the splitter. As a result the splitter is better able to absorb lateral forces.
  • a sectional component according to the invention can have a capping plate, which joins the top edges of the side walls to one another.
  • a sectional component is suitable for the top sectional component, viewed in the height direction.
  • the capping plate then forms a cover for closing off the top side of the splitter. In this case the splitter is delimited by a closed housing.
  • the side walls are provided with the perforations and the slanted side edges and/or the slanted top edges are unperforated.
  • the unperforated edges form a welding surface, over which several welds, made some distance apart in the longitudinal direction can join two stacked sectional components.
  • the sectional components are each made from a flat sheet.
  • a punching machine first punches out the perforations in the sheet at the location of the portions that will form the side walls of the splitter. During this operation local stress concentrations are introduced into the sheet.
  • the sheet provided locally with perforations is then bent, the slanted side edges and/or the slanted top edges being produced. Because said edges are not perforated, that is to say there are no perforations along the bend line, bending can take place along a straight line. After all, because of the stress concentrations bending along perforations would proceed out of true and not in a fully controlled manner.
  • the invention also relates to a sectional component clearly intended for use with a splitter as described above.
  • the invention relates to a gas turbine, comprising an inlet, a compressor, a combustion chamber, a turbine as well as an exhaust, in which a sound damper as described above has been fitted.
  • the invention relates to a method for the production of a splitter as described above, comprising the provision of a sheet with a length dimension L and a width dimension B, for example standard dimensions available commercially, converting the sheet into a sectional component with a number of section walls, where the sum of the dimensions of the section walls corresponds to the length dimension L or the width dimension B of the sheet.
  • This method leads to a minimum of waste.
  • an exhaust 1 of a gas turbine has a feed end 2 and a discharge end 3.
  • the exhaust 1 can be arranged either horizontally or vertically. Air enters the exhaust 1 from the turbine of the gas turbine at the feed end 2, for example at a speed of 50 - 70 m/s. The air flows through the exhaust 1 and leaves this through the discharge end 3, which, for example, opens into a discharge channel or a chimney of a power station (not shown).
  • the rotating components of the gas turbine create enormous noise.
  • the sound power at the feed end 2 of the exhaust 1 can be 150 dB or more.
  • a sound damper 4 has been accommodated in the exhaust 1.
  • the sound damper 4 shown in Figure 1 has three splitters 5 (German: Kulissen), a greater or smaller number of splitters can, of course, be provided.
  • Each splitter 5 is made up of several sectional components 6, which bear directly on one another (see also Figure 3).
  • Each sectional component 6 comprises a thin-walled, trough-shaped bar. This trough-shaped bar is open on one longitudinal side.
  • the panel By stacking the sectional components 6 on top of one another the panel has tubular shapes adjoining one another in cross-section. This results in a lightweight splitter that is flexible in the transverse direction but is still adequately rigid. Stacking of this illustrative embodiment will be described in more detail below.
  • Thin-walled must be understood to mean a wall thickness that enables flexibility of the splitter. This wall thickness is, for example, 1 - 4 mm, such as 2 or 3 mm.
  • Such a splitter 5 has a greater flexibility than a conventional splitter that is made up as a framework.
  • the splitter according to the invention is able to give under the influence of lateral stress on the splitter. As a result the splitter according to the invention will be less liable to crack as a consequence of sudden changes in temperature.
  • the trough-shaped sectional components 6 each surround an interior 7 in which a sound-damping material, such as mineral wool, is accommodated. It is also possible that this sound-damping material is arranged in a closed envelope to form a sound-damping cushion. Filling the interior 7 of the sectional components 6 with cushions instead of loose mineral wool prevents irritation of the hands as a result of contact with said wool.
  • a sound-damping material such as mineral wool
  • the side walls 8 of the splitters 5 are provided with perforations 9.
  • the perforations 9 preferably each have a diameter of between 2 and 4 mm. The sound can penetrate through the perforations 9 into the interior 7 of the sectional components 6, where the mineral wool damps the sound.
  • a splitter 5 according to the invention is made up as follows. First of all a bottom sectional component 6 is placed on a bearing surface. The sound-damping material is then placed via the open longitudinal side of said trough-shaped sectional component 6 in the interior 7 thereof. A further sectional component 6 is then stacked on top of the bottom sectional component 6 so that the interior 7 thereof is closed off. This further sectional component 6 can then be filled, etc. It is also possible first to fill several or all sectional components 6 required for the splitter 5 and then to stack the sectional components 6 on top of one another.
  • the stacking according to this illustrative embodiment is shown most clearly in Figure 3.
  • the sectional components 6 have shaped parts, which engage with one another, at the stacking ends 20, 21 stacked on top of one another.
  • the bottom of the sectional component 6 forms the first stacking end 20, whilst the top of the sectional component 6 forms the second stacking end 21.
  • the sectional components 6 each have a base 10, which has slanted side edges 11 on either side thereof.
  • the side edges 11 are joined to respective upright side walls 12, which at the top thereof each pass into a slanted top edge 14.
  • the slanted top edges 14 are oriented towards one another, the side edges 11 of a sectional component 6 on top of them being enclosed between said top edges 14.
  • the base 10 of the sectional component 6 on top is thus arranged between the top edges 14 of the underlying sectional component 6 to some extent in the interior 7 thereof.
  • the side edges 11 and top edges 14 form stacking edges of the sectional component 6.
  • the edges 11, 14 act as reinforcing flanges that increase the strength and rigidity of the splitter 5 according to the invention.
  • the top sectional component 6 (see Figures 1, 4a, 4b) is closed off by a flat capping plate 13.
  • the capping plate 13 forms a lid so that the sound-damping material is not able to escape from the top sectional component.
  • Figures 2 and 3 furthermore show that the side edges 11 and the top edges 14 are unperforated.
  • the sectional components 6 are welded to one another by welds 16 at the location of said unperforated side edges 11 and top edges 14.
  • the sectional components 6 can be fitted in an essentially rectangular guide frame 17.
  • This frame 17 has two vertical uprights as well as two longitudinal sections on the top and bottom of the frame 17, respectively.
  • the frame 17 guarantees that the sectional components are stacked aligned with respect to one another.
  • the sectional components 6 extend in the longitudinal direction of the splitter 5, which means that the air flows from the feed end 4 to the discharge end 3 essentially in the longitudinal direction of the sectional components 6.
  • the exhaust 1 can also be arranged vertically, the sectional components 6 being arranged with the end faces thereof between the upright side walls of the exhaust (not shown). With this arrangement the air flow is oriented transversely with respect to the longitudinal direction of the sectional components.
  • the longitudinal direction of the sectional components and the longitudinal direction of the exhaust can then be perpendicular with respect to one another, such as essentially horizontal and vertical, respectively.
  • the approach side of the splitter 5 can therefore be formed either by the end faces of the sectional components 6 or by the top or bottom of the sectional components 6.
  • the approach side can be provided with a rounded streamlining piece 18 (see Figures 4a, 4b).
  • This rounded shape has five angularly offset segments 19.
  • the streamlining piece 18 can also have another shape.
  • Figure 4a the streamlining piece 18 is fitted against the base of the bottom sectional component 6.
  • the approach to the splitter 5 is thus from bottom to top according to arrow A.
  • Figure 4b shows that the streamlining piece 18 can also be integrated with the bottom sectional component 6. In this case the bottom sectional component 6 itself has a rounded shape.
  • the splitter 5 can also have a streamlining piece on the outflow side facing away from the approach side, close to the outflow opening.
  • the streamlining piece 18 is particularly advantageous in the case of high air speeds.
  • the streamlined front edge reduces the disturbance of the airflow, as a result of which the resistance is lower and the air warms up to a lesser extent as a result of collision with the front edge.
  • a streamlined rear wall has a corresponding advantageous effect.
  • the sectional components 6 are preferably made of a bent sheet or plate, for example stainless steel, steel or aluminium.
  • This sheet has a thickness of, for example, 3 mm.
  • Figure 5a shows a flat, rectangular sheet that has been made from stainless steel.
  • the sheet has a length dimension L of 3000 mm and a width dimension B of 1500 mm.
  • First of all longitudinal bands of perforations 30, 31 are punched or stamped in the sheet in the longitudinal direction, leaving unperforated longitudinal bands 32-36. After perforation, the sheet is bent along the bend lines 40 to give the sectional component 6 shown in Figure 5b. Because there are no perforations along the bend lines 40, bending can take place in a controlled manner and in a straight line.
  • the sectional component 6 according to Figure 5b has a base 44, two slanted side edges 43, 45, two side walls 40, 41 and two top edges 42, 46.
  • This sectional component is trough-shaped, a slot-shaped opening having been formed at the end facing away from the base. Stacking of such sectional components is shown in Figures 1 - 3.
  • the longitudinal bands with perforations 30, 31 correspond to the side walls 40, 41 of this sectional component, whilst the other longitudinal bands 32-36 correspond to the top edge 42, the side edge 43, the base 44, the side edge 45 and the top edge 46 of this sectional component, respectively.
  • the sum of the dimensions of the base 44, two slanted side edges 43, 45, two side walls 40, 41 and two top edges 42, 46 is equal to the width dimension of the sheet, in this case 1500 mm.
  • This sectional component 6 has therefore been formed without loss of material.
  • the dimensions LxB are, for example, standard dimensions available commercially, such as 1000 x 1000 mm, 2000 x 1000 mm or 1500 x 3000 mm.
  • the dimensions LxB according to the invention can also be dimensions that are not available commercially but are ordered to size.
  • the dimensions of the sheet can be chosen by the designer depending on the total length of the exhaust.
  • the sound damper has been described above for the exhaust for a gas turbine, the sound damper according to the invention is suitable for any application where sound has to be absorbed. According to the invention the sound damper described above can, for example, also be installed in the exhaust of a diesel engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust Silencers (AREA)
EP05107559A 2004-08-19 2005-08-17 Schalldämpfer, Durchschnittbauelement und Herstellungsverfahren einer Kulisse Active EP1628004B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL1026879A NL1026879C2 (nl) 2004-08-19 2004-08-19 Geluiddemper, profieldeel en werkwijze voor het vervaardigen van een paneel.

Publications (2)

Publication Number Publication Date
EP1628004A1 true EP1628004A1 (de) 2006-02-22
EP1628004B1 EP1628004B1 (de) 2010-04-14

Family

ID=34974134

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05107559A Active EP1628004B1 (de) 2004-08-19 2005-08-17 Schalldämpfer, Durchschnittbauelement und Herstellungsverfahren einer Kulisse

Country Status (4)

Country Link
EP (1) EP1628004B1 (de)
AT (1) ATE464463T1 (de)
DE (1) DE602005020550D1 (de)
NL (1) NL1026879C2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008065361A1 (en) * 2006-12-01 2008-06-05 Robert Bosch Gmbh Thermal acoustic baffle
AT513843B1 (de) * 2013-05-06 2014-08-15 Compact Power Plant Products Gmbh Schalldämpfer für einen Abgaskanal
US11139718B2 (en) 2017-07-21 2021-10-05 Siemens Industry, Inc. Electric machine with auxiliary blower mounting arrangement and/or modular exhaust assembly

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2303611A1 (de) * 1973-01-25 1974-08-15 Costa Silard Dipl I Vasiljevic Schalldaempfer
FR2447069A1 (fr) * 1979-01-16 1980-08-14 Westeel Guy Perfectionnements aux dispositifs d'insonorisation disposes dans des ecoulements fluides
DE2932439A1 (de) * 1979-08-10 1981-02-26 Luefa Werke Gmbh Kulissenschalldaempfer fuer stroemende gase
DE19818415A1 (de) * 1998-04-24 1999-01-14 Gerd Raichle Verbrennungsgeräuschminderer für Kessel-Brennereinheiten
WO1999035378A1 (en) * 1997-12-30 1999-07-15 Silentor Notox A/S A silencer
US20030039595A1 (en) * 2001-08-24 2003-02-27 Geise C. Joseph Modular exhaust treatment system
US20030072648A1 (en) * 2001-05-30 2003-04-17 Han Ming Hui Outlet silencer structures for turbine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2303611A1 (de) * 1973-01-25 1974-08-15 Costa Silard Dipl I Vasiljevic Schalldaempfer
FR2447069A1 (fr) * 1979-01-16 1980-08-14 Westeel Guy Perfectionnements aux dispositifs d'insonorisation disposes dans des ecoulements fluides
DE2932439A1 (de) * 1979-08-10 1981-02-26 Luefa Werke Gmbh Kulissenschalldaempfer fuer stroemende gase
WO1999035378A1 (en) * 1997-12-30 1999-07-15 Silentor Notox A/S A silencer
DE19818415A1 (de) * 1998-04-24 1999-01-14 Gerd Raichle Verbrennungsgeräuschminderer für Kessel-Brennereinheiten
US20030072648A1 (en) * 2001-05-30 2003-04-17 Han Ming Hui Outlet silencer structures for turbine
US20030039595A1 (en) * 2001-08-24 2003-02-27 Geise C. Joseph Modular exhaust treatment system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
FUCHS H V ET AL: "NICHTPOROSER SCHALLABSORBER FUR DEN EINSATZ IN RAUCHGASREINIGUNGSANLAGEN", 1 November 1989, VGB KRAFTWERKSTECHNIK, VGB KRAFTWERKSTECHNIK GMBH. ESSEN, DE, PAGE(S) 1102-1110, ISSN: 0372-5715, XP000083750 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008065361A1 (en) * 2006-12-01 2008-06-05 Robert Bosch Gmbh Thermal acoustic baffle
AT513843B1 (de) * 2013-05-06 2014-08-15 Compact Power Plant Products Gmbh Schalldämpfer für einen Abgaskanal
AT513843A4 (de) * 2013-05-06 2014-08-15 Compact Power Plant Products Gmbh Schalldämpfer für einen Abgaskanal
WO2014179821A1 (de) * 2013-05-06 2014-11-13 Compact Power Plant Products Gmbh Schalldämpfer für einen abgaskanal
US11139718B2 (en) 2017-07-21 2021-10-05 Siemens Industry, Inc. Electric machine with auxiliary blower mounting arrangement and/or modular exhaust assembly

Also Published As

Publication number Publication date
NL1026879C2 (nl) 2006-02-21
DE602005020550D1 (de) 2010-05-27
EP1628004B1 (de) 2010-04-14
ATE464463T1 (de) 2010-04-15

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