EP2240696A1 - Manchon d'admission pour compresseur axial - Google Patents

Manchon d'admission pour compresseur axial

Info

Publication number
EP2240696A1
EP2240696A1 EP08872325A EP08872325A EP2240696A1 EP 2240696 A1 EP2240696 A1 EP 2240696A1 EP 08872325 A EP08872325 A EP 08872325A EP 08872325 A EP08872325 A EP 08872325A EP 2240696 A1 EP2240696 A1 EP 2240696A1
Authority
EP
European Patent Office
Prior art keywords
inlet
bearing
housing
inlet nozzle
fluid
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
EP08872325A
Other languages
German (de)
English (en)
Other versions
EP2240696B1 (fr
Inventor
C. Lange
Henning Ressing
Fikri Aynacioglu
Dirk Anding
Karl-Heinz Dreyer
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.)
Everllence SE
Original Assignee
MAN Diesel and Turbo SE
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 MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP2240696A1 publication Critical patent/EP2240696A1/fr
Application granted granted Critical
Publication of EP2240696B1 publication Critical patent/EP2240696B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • 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
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • 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
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/644—Mounting; Assembling; Disassembling of axial pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations

Definitions

  • the invention relates to an inlet connection for an axial compressor, in particular a turbocompressor, with an inlet housing, in which a bearing housing with a fluid axially in the flow direction of the first bearing for a rotor of the axial compressor is arranged, wherein the bearing housing with the inlet housing is connected via an inlet strut, which is connected in a front cross-section with the inlet housing.
  • Such intake struts are purely radial in conventional axial compressors, ie. parallel to a normal plane to the longitudinal axis of the inlet nozzle, so that the bearing center of the first or front bearing is arranged axially in the flow direction of a fluid to be compressed substantially at the level of the center of area of this end cross-section, in other words the bearing axially centrally in the inlet strut under the transition is arranged in the inlet housing.
  • a piercing point of a bearing axis by a symmetry plane of a symmetrical bearing, a center of gravity of the bearing, the geometric center between the axial end faces of the bearing or a pressure point of the bearing are referred to as the bearing center point.
  • the inlet struts in particular for reasons of strength and production, are often axially connected relatively far forward to the inlet cross-section of the inlet connection with the inlet housing in order to be able to support against corresponding reinforcements of the inlet housing or to avoid greatly varying wall thicknesses during prototyping, this is also the first or front bearing arranged correspondingly far forward, so that there is a relatively large bearing distance to a second, rear bearing of the rotor of the axial compressor, which is arranged in the flow direction behind the first bearing.
  • one or more fluid passages may be formed.
  • Such fluid passages can serve, for example, the lubrication of the bearing and this on the one hand in or close to the bearing in the bearing housing open and on the other hand with a Schmierffenver- or disposal, for example via grease nipple, lines, passages in adjacent housing parts o- the like, be connected outside of the inlet housing.
  • a Schmierstoffver- or disposal for example via grease nipple, lines, passages in adjacent housing parts o- the like, be connected outside of the inlet housing.
  • a bearing supplied by the radial fluid passage has to be arranged axially at the level of the outlet opening of the fluid passage from the inlet housing, which also disadvantageously increases the bearing center distance of the rotor.
  • Object of the present invention is therefore to provide an improved inlet nozzle available.
  • an inlet nozzle according to the preamble of claim 1 is further developed by at least one of its characterizing features.
  • Claim 14 provides an axial compressor with such an inlet connection under protection, the dependent claims relate to advantageous developments.
  • An inlet connection according to the invention is provided for an axial compressor, in particular a turbocompressor, and may preferably be detachably or fixedly connected or integrally formed therewith. It has an inlet housing, the interior of which preferably tapers in the flow direction of a fluid to be compressed.
  • a bearing housing is arranged, which receives a front or first bearing for a rotor of the axial compressor. This may in particular be a radial bearing, a thrust bearing or a radial-axial bearing.
  • This bearing is axially in the flow direction of a fluid to be compressed, a first, ie front bearing, wherein the rotor may be supported in other camps, which have a greater axial distance to an inlet cross-section of the inlet nozzle.
  • the bearing housing is supported in the inlet housing via one or more inlet struts. Several inlet struts can be distributed equidistantly over the circumference of the bearing housing or have different angular distances from each other.
  • inlet struts While equidistantly distributed inlet struts the flow in the bearing housing homogeneous and thus little disturbing, inlet struts with different angular distances to each other can be adapted to structural constraints of the housing, especially external leads, ribs, different wall thicknesses or the like.
  • One or more inlet struts are each connected to the inlet housing in one end section of the corresponding inlet strut.
  • one or more, preferably all inlet struts may be integrally connected to the inlet and / or bearing housing, for example by primary molding.
  • one or more inlet struts can also be connected to the entry and / or bearing housing after the prototyping, for example welded or screwed.
  • the bearing center of the first bearing in the flow direction of a fluid to be compressed is now axially at least 0.1 times, preferably at least 0.15 times, more preferably at least 0.2 times and in particular arranged at least 0.25 times the chord length of the end cross-section behind the center of area of the end cross-section.
  • the chord length is the maximum extent of the end cross-section in the axial direction, ie. in the flow direction of a fluid to be compressed, which corresponds to its diameter, for example, in the case of a circular end cross-section, and in the case of an elliptical front cross-section to its large radius.
  • the first bearing behind the center of area of an end cross-section. This advantageously reduces the bearing distance to the center of mass of the rotor and, if present, to a second, rear bearing of the rotor of the axial compressor, which is arranged behind the first bearing in the direction of flow.
  • the first bearing may be behind the first two-thirds of the chord length, ie at least 0.17-fold, preferably behind the first three The length of the chord, ie at least 0.25 times behind the center of the face of the end cross-section.
  • the bearing center point of the first bearing is axially at least 0.1 times, 0.15 times, 0.2 times or 0 , 25 times the chord length of the end cross section behind the center of area of the end cross-section of at least one inlet strut arranged.
  • inlet struts it is also possible for inlet struts to be present, with respect to whose end cross-section the first bearing is arranged axially in front of or in the center of the surface.
  • the bearing center of the first bearing is arranged axially at least 0.1 times, 0.15 times, 0.2 times or 0.25 times the chord length of the end cross section behind the surface centers of the end cross sections of all inlet struts ,
  • the bearing center no longer has to lie within the chord length of the end section (s) projected onto the longitudinal axis of the entry socket, but can also be arranged axially behind the end section (s). Equally, however, it can also be located within the chord length of the end cross-section or sections projected onto the longitudinal axis of the entry stub, in particular at most 0.75 times, in particular at most 0.5 times the chord length of the end cross-section, behind the center of area of the end cross section be.
  • a fluid passage is formed in at least one inlet struts. This can be provided in particular for supplying and / or removing lubricant to the bearing for the impeller.
  • a fluid passage can likewise serve for supplying and / or removing cooling fluid, in particular cooling air, and / or a blocking fluid, in particular blocking air, in order to cool the axial compressor or to avoid a lubricant outlet into the axial compressor.
  • Other fluids such as a hydraulic fluid, in particular a controlled bearing, can flow through the fluid passage.
  • a fluid passage in a preferred embodiment in or in the vicinity of the bearing can open into the bearing housing.
  • the fluid passage is also designed, for example, to guide cables, lines or the like, for example electrical and / or optical lines for sensors in the bearing housing.
  • such a fluid passage at least in sections forms an acute angle with a normal plane to the longitudinal axis of the inlet nozzle, i. extends obliquely to the axial direction of the inlet nozzle, in particular from radially outward to radially inward in the flow direction of the fluid to be compressed.
  • the first and second embodiments may advantageously be combined with each other. If the first bearing according to the first embodiment is offset axially rearward relative to the end cross-section of an inlet strut, it can be operated particularly well by obliquely extending fluid passages in this inlet strut. However, in the first embodiment, if the cross section of an inlet strut permits it, fluid passages may also be purely radial or, conversely, oblique fluid passages may be provided in purely radially aligned inlet struts in which the bearing center lies axially below the area center of the end cross section. In this respect, the following explanations apply equally to the first and / or second embodiment of the present invention.
  • fluid passages can be formed in one or more inlet struts, wherein at least one, preferably several, particularly preferably all fluid passages form an acute angle with a normal plane to the longitudinal axis of the inlet nozzle.
  • Such fluid passages may preferably run substantially parallel to one another, which is the production simplified. Likewise, however, they may also include different angles with the normal plane so as to define in particular optimal paths between exit positions on the inlet housing and on the bearing housing. In this way, for example, fluid passages opening into the bearing housing close to one another can be connected to supply lines at the inlet housing which are axially remote from one another, and vice versa.
  • fluid passages in two inlet struts may be formed so as to optimally distribute, for example, supply and discharge lines. Also fluid passages in the same or different inlet struts need not have the same diameter, but may, for example, be adapted to the nature and quantity of the added or discharged medium.
  • One or more fluid passages may be substantially rectilinear so as to form the same acute angle everywhere with a normal plane to the longitudinal axis of the inlet nozzle. Such fluid passages are particularly easy to produce by drilling and to consider in the design.
  • the angle formed by such a substantially rectilinear fluid passage with a normal plane to the longitudinal axis of the inlet nozzle can preferably be in the range between 10 ° and 40 °, in particular in the range between 20 ° and 30 °. This represents a good compromise from shortening the bearing center distance and increasing the manufacturing effort.
  • One or more fluid passages may also have a kinked profile, so that at least a portion of this fluid passage forms an acute angle with a normal plane to the longitudinal axis of the inlet nozzle.
  • other sections of such fluid passages for example, can extend substantially in the radial direction of the inlet housing. In this way, the advantages of purely radial and inclined fluid passages can be interconnected.
  • the angle which forms such an oblique section of a fluid passage with a bent course with a normal plane to the longitudinal axis of the inlet nozzle is preferably in the range between 60 ° and 80 °, in particular in the range between 65 ° and 75 °. Since here only a shorter distance in the radial direction to compensate for the axial offset between inlet and outlet of the fluid passage available stands, such oblique sections preferably have larger angles to the normal plane than kinkless fluid passages.
  • two or more fluid passages open into a common portion that communicates with the interior of the bearing housing.
  • this section may extend obliquely, while the fluid passages opening into it preferably extend essentially in the radial direction of the inlet housing.
  • a radial axis through the center of gravity or gravity of at least one inlet strut can also - at least in sections - form an acute angle with a normal plane to the longitudinal axis of the inlet nozzle
  • Such a swept inlet strut is particularly suitable for receiving in particular straight-line fluid passages.
  • an inlet strut can also extend substantially in the radial direction of the inlet housing and widen towards the bearing housing, so that the center of area or center of gravity displaced towards the bearing housing in the flow direction of a fluid to be compressed to the rear.
  • Figure 1 shows an inlet nozzle according to an embodiment of the present invention in half section.
  • Fig. 2 shows the inlet nozzle of FIG. 1 in perspective quarter section.
  • FIG. 2 shows the lower cut-out lower, seen in the flow direction of a fluid to be compressed, of an inlet connection piece according to an embodiment. tion of the present invention in a perspective view, Fig. 1 is a horizontal section in Fig. 2nd
  • the inlet nozzle has an inlet housing 1 for collecting and supplying a medium to a turbo-compressor (not shown).
  • a bearing housing 2 is arranged which has a substantially cylindrical shape, with the medium to be compressed in the flow direction (from the left to the right in the figures), front hemispherical front side has.
  • a radial bearing 3 for a rotor with impeller of the turbocompressor (not shown) is formed, the bearing center point 3a is located axially in the center of the bearing ring shown.
  • the bearing housing 2 is connected to the inlet housing 1 via three, four or more inlet struts, wherein in Fig. 2, a lower (cut) and a left (partially hidden) inlet strut 4 can be seen, in Fig. 1, the left inlet strut 4.
  • two or more blind struts are additionally arranged in the upper half of the inlet housing, which are not connected to the bearing housing.
  • the illustrated in Fig. 1 left inlet strut 4 is integrally connected to the inlet housing 1 and is in its the inlet housing 1 facing end cross-section in this over.
  • the center of area 10 of this end cross-section is shown in Fig. 1 and is located axially in front of the bearing center 3a, which is offset from the center of area 10 by 0.375 times in the flow direction of a fluid to be compressed axially to the rear (to the right in Fig. 1).
  • three fluid passages 5 are formed, of which one in Fig. 1 left, front fluid passage 5.1 (dash-dotted lines in Fig.
  • a middle fluid passage 5.2 (shown in FIG. 1) serves the supply of lubricant to the bearing 3 and opens into the bearing 3 in the bearing housing 2, and a right in Fig. 1, rear fluid passage 5.3 (dash-dotted lines in FIG 1) the supply of sealing air into the bearing housing 2 and in the vicinity of the bearing 3 after this opens into the bearing housing 2.
  • These fluid passages 5 are formed as through-holes and therefore extend substantially straight. They include an acute angle of about 23 ° with a normal plane to the longitudinal axis of the inlet nozzle (vertical plane perpendicular to the plane of FIG. 1) or the complementary angle of about 67 ° with the longitudinal axis.
  • two fluid passages 6 are formed, which serve for the removal of lubricant from the interior of the bearing housing 2.
  • These fluid passages 6 form sections an acute angle with a normal plane to the longitudinal axis of the inlet nozzle. For this purpose, they have a kinked course, wherein in each case a substantially extending in the radial direction portion 61 and 6.2 merges into a two fluid passages 6 common portion 8, which forms an acute angle of about 72 ° with a normal plane to the longitudinal axis of the inlet nozzle ,
  • This common inclined section 8 extends in the longitudinal direction of the inlet housing 1 (from left to right in FIG. 1) and terminates in a circular segment-shaped annular groove 7, which is formed at right angles to the section 8 and extends over a range of 70 ° in FIG the lower half of the bearing housing 2 extends.
  • a circular segment-shaped annular groove 7 which is formed at right angles to the section 8 and extends over a range of 70 ° in FIG the lower half of the bearing housing 2 extends.
  • common open portion 8 which extends from the annular groove 7 below the radial bearing 3 forward through to the extending in the radial direction sections 6.1, 6.2, communicate the two fluid passages with the interior of the bearing housing. 2
  • the bearing center of the bearing 3 as seen in Fig. 2, axially offset to the rear and is in the last third of its projected to the longitudinal axis 9 chord length.
  • the inlet struts 4 extend essentially in the radial direction (from top to bottom in FIG. 1).
  • the inlet struts 4 In order to have sufficient material for the oblique fluid passages 5 and the oblique, common section 8 and to support the bearing center well on both sides, the inlet struts 4 at their in the flow direction of the fluid to be compressed (right in Fig. 1, 2 ) rear trailing edge a substantially dreickförmigen approach 4.1.
  • a radial axis through the surface centers of the inlet struts 4 therefore has in this section with the paragraph 4.1 at an acute angle with a normal plane to the longitudinal axis of the inlet nozzle.
  • Fluid passage for air, lubricant or cable

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un manchon d'admission pour compresseur axial, notamment pour un turbocompresseur, cet manchon comportant un boîtier d'admission (1) dans lequel est logé un boîtier de palier (2) comportant un palier (3), notamment un palier radial et/ou axial, pour un rotor, le boîtier de palier (2) étant relié au boîtier d'admission (1) par un montant d'admission (4) relié au boîtier d'admission dans une section transversale frontale. Le centre du palier (3) est, dans le sens de l'écoulement d'un fluide à comprimer, disposé axialement à au moins 0,1 fois, notamment au moins 0,15 fois, notamment au moins 0,2 fois, notamment au moins 0,25 fois la longueur de corde de la section transversale frontale derrière le point central de la surface de la section transversale frontale. En outre ou en alternative, un passage fluidique (5,6) est ménagé dans le montant d'admission (4), ce passage fluidique (5,6) formant au moins partiellement un angle aigu avec un plan normal relativement à l'axe longitudinal de la manchon d'admission.
EP08872325.9A 2008-02-13 2008-11-03 Manchon d'admission pour compresseur axial Not-in-force EP2240696B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810008886 DE102008008886A1 (de) 2008-02-13 2008-02-13 Eintrittsstutzen für einen Axialverdichter
PCT/EP2008/009254 WO2009100741A1 (fr) 2008-02-13 2008-11-03 Manchon d'admission pour compresseur axial

Publications (2)

Publication Number Publication Date
EP2240696A1 true EP2240696A1 (fr) 2010-10-20
EP2240696B1 EP2240696B1 (fr) 2019-01-02

Family

ID=40350157

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08872325.9A Not-in-force EP2240696B1 (fr) 2008-02-13 2008-11-03 Manchon d'admission pour compresseur axial

Country Status (6)

Country Link
US (1) US9004856B2 (fr)
EP (1) EP2240696B1 (fr)
JP (1) JP5444254B2 (fr)
CN (1) CN101952604B (fr)
DE (1) DE102008008886A1 (fr)
WO (1) WO2009100741A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008008886A1 (de) 2008-02-13 2009-08-20 Man Turbo Ag Eintrittsstutzen für einen Axialverdichter

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GB583469A (en) * 1943-01-04 1946-12-19 David Macleish Smith Improvements in turbo compressors
US2648493A (en) * 1945-10-23 1953-08-11 Edward A Stalker Compressor
US2665549A (en) * 1949-11-02 1954-01-12 United Aircraft Corp Compressor drive and fuel supply for gas turbine power plants
DE2242734A1 (de) * 1972-08-31 1974-03-21 Motoren Turbinen Union Lagerung fuer waermekraftmaschinen
EP0122328B1 (fr) * 1979-05-14 1987-03-25 OSBORN, Norbert Lewis Carter de compresseur pour une turbosoufflante ainsi que méthode de production d'un tel carter
CN1004016B (zh) * 1985-04-01 1989-04-26 苏舍兄弟有限公司 涡轮机的筒形外壳
US4868963A (en) * 1988-01-11 1989-09-26 General Electric Company Stator vane mounting method and assembly
FR2631386A1 (fr) * 1988-05-11 1989-11-17 Snecma Turbomachine comportant une grille d'entree incorporant des tubes de passage d'huile
US5253985A (en) * 1990-07-04 1993-10-19 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Exhaust gas turbocharger having rotor runners disposed in roller bearings
US6030176A (en) * 1995-07-19 2000-02-29 Siemens Aktiengesellschaft Structural member for an exhaust-gas connection of a turbomachine, in particular a steam turbine, and set of at least two structural members
GB2324833B (en) * 1997-02-22 2000-10-04 Rolls Royce Plc Gas turbine engine support structure
US6330790B1 (en) * 1999-10-27 2001-12-18 Alliedsignal, Inc. Oil sump buffer seal
IT1318110B1 (it) * 2000-07-03 2003-07-23 Nuovo Pignone Spa Sistema di scarico e di refrigerazione per i cuscini di una turbina agas
EP1186781B2 (fr) * 2000-09-08 2012-05-30 ABB Turbo Systems AG Dispositif de montage d'un filtre silencieux pour l'entrée d'une turbo-soufflante
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DE102008008886A1 (de) 2008-02-13 2009-08-20 Man Turbo Ag Eintrittsstutzen für einen Axialverdichter

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Title
See references of WO2009100741A1 *

Also Published As

Publication number Publication date
DE102008008886A1 (de) 2009-08-20
CN101952604A (zh) 2011-01-19
US20100329861A1 (en) 2010-12-30
CN101952604B (zh) 2013-11-06
EP2240696B1 (fr) 2019-01-02
WO2009100741A1 (fr) 2009-08-20
JP5444254B2 (ja) 2014-03-19
JP2011511899A (ja) 2011-04-14
US9004856B2 (en) 2015-04-14

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