EP1866545B1 - Flow stabilization system for centrifugal compressor - Google Patents
Flow stabilization system for centrifugal compressor Download PDFInfo
- Publication number
- EP1866545B1 EP1866545B1 EP06705411.4A EP06705411A EP1866545B1 EP 1866545 B1 EP1866545 B1 EP 1866545B1 EP 06705411 A EP06705411 A EP 06705411A EP 1866545 B1 EP1866545 B1 EP 1866545B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- injection
- orifice
- flow passage
- casing wall
- 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.)
- Not-in-force
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Classifications
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- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
-
- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
-
- 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
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
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- 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
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
- F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
- F04D27/0238—Details or means for fluid reinjection
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- 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
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
- Y10S415/914—Device to control boundary layer
Description
Die Erfindung bezieht sich auf das Gebiet der Radialverdichter von Abgasturboladern. Sie betrifft eine Vorrichtung zum Einblasen von Luft in den Strömungskanal eines Radialverdichters gemäss dem Oberbegriff des Patentanspruchs 1.The invention relates to the field of centrifugal compressors of exhaust gas turbochargers. It relates to a device for blowing air into the flow channel of a centrifugal compressor according to the preamble of patent claim 1.
Um die Kennfeldbreite von Radialverdichterstufen zu erhöhen, kommen in einer Vielzahl von Radialverdichterstufen der neusten Generationen Stabilisatoren im Ansaugbereich des Verdichterrades zum Einsatz.In order to increase the map width of radial compressor stages, stabilizers are used in the intake of the compressor wheel in a variety of radial compressor stages of the latest generations.
Die Nachfrage vom Markt für stetig höhere Druckverhältnisse bei Verdichtern von Abgasturboladern ist ungebrochen. Der Erhöhung des Druckverhältnisses über eine Erhöhung der Drehzahl bei unverändertem Verdichterstufendesign sind jedoch Grenzen gesetzt, da die das nutzbare Kennfeld begrenzende Pump- und Schluckgrenze mit zunehmender Drehzahl zusammenlaufen. Die nutzbare Kennfeldbreite nimmt somit in Richtung höherer Druckverhältnisse kontinuierlich ab. Um dem entgegenzuwirken und das nutzbare Kennfeld auch bei hohen Druckverhältnissen möglichst breit zu halten, kann bei gleichbleibendem Verdichterraddesign und unveränderter Verdichterradgrösse ein Diffusor mit kleinerem Strömungsquerschnitt eingesetzt werden. Die Pumpgrenze verschiebt sich dadurch zu kleineren Volumenströmen und es resultiert bei gleichbleibender Radschluckgrenze eine grössere nutzbare Kennfeldbreite. Nachteilig ist dabei, dass sich der Wirkungsgrad verringert, insbesondere bei Teillast. Dieser Nachteil kann vermieden werden, indem durch geeignete Massnahmen die Stabilität der gegebenen Verdichterstufen bei Maximallast erhöht wird. Dies kann durch gehäuseseitiges Einblasen von Luft in den Strömungskanal im unbeschaufelten Zwischenraum zwischen den Laufschaufeln des Verdichterrades und den Leitschaufeln des Diffusors geschehen. Die dynamische Stabilität im Bereich hoher Druckverhältnisse kann durch das Einblasen von Luft erhöht werden.The demand from the market for steadily higher pressure ratios in compressors of exhaust gas turbochargers is unbroken. However, there are limits to increasing the pressure ratio by increasing the speed when the compressor stage design is unchanged, since the pumping and intake limits limiting the usable characteristic field converge with increasing engine speed. The usable characteristic map width thus decreases continuously in the direction of higher pressure conditions. To counteract this and to keep the usable map as wide as possible even at high pressure conditions, a diffuser with a smaller flow cross-section can be used with constant compressor wheel design and unchanged Verdichterradgrösse. As a result, the pumping limit shifts to smaller volume flows, resulting in a larger usable characteristic map width while maintaining the wheel slip limit. A disadvantage is that the efficiency is reduced, especially at partial load. This disadvantage can be avoided by appropriate measures to increase the stability of the given compressor stages at maximum load. This can be done by injecting air from the housing into the flow channel in the unopened space between the blades of the compressor wheel and the vanes of the diffuser. The dynamic stability in the range of high pressure conditions can be increased by the injection of air.
Eine andere Möglichkeit zur Erhöhung des Druckverhältnisses und Vermeidung des Zusammenlaufens von Pump- und Schluckgrenze ist die Anpassung des Verdichterraddesigns. Die Stabilität und damit die nutzbare Kennfeldbreite lässt sich durch eine Erhöhung des "Backsweep" beim Verdichterrad erreichen. "Backsweep" bezeichnet den Winkel am Verdichterradaustritt zwischen einer Schaufel mit radial stehender Hinterkante und einer mit entgegen der Raddrehrichtung in tangentialer Richtung flacher gestelltem Austrittswinkel. Die Erhöhung des "Backsweep" hat zur Folge, dass zur Erreichung eines gleichen Druckverhältnisses eine Erhöhung der Radumfangsgeschwindigkeit nötig ist. Damit ist zur Erreichung eines höheren Druckverhältnisses eine überproportionale Erhöhung der Drehzahl erforderlich. Dem sind aber Grenzen seitens des Verdichterradmaterials gesetzt, respektive es muss auf ein Material mit besseren mechanischen Eigenschaften gewechselt werden. Solche Materialien sind wesentlich teurer. Gegenüber dieser Lösung zeigt das Einblasen von Luft Kostenvorteile, da eine bestehende Verdichterstufe zur Erreichung höherer Druckverhältnisse ertüchtigt wird und der kostspielige Materialwechsel beim Verdichterrad vermieden werden kann.Another way to increase the pressure ratio and avoid the convergence of the pumping and swallowing limit is to adapt the compressor wheel design. The stability and thus the usable map width can be achieved by increasing the backsweep in the compressor wheel. "Backsweep" refers to the angle at the compressor wheel outlet between a blade with a radially standing trailing edge and an outlet angle which is made flatter in the tangential direction opposite to the wheel rotation direction. The increase of the "backsweep" has the consequence that in order to achieve an equal pressure ratio an increase in the wheel circumference speed is necessary. This is to achieve a higher pressure ratio, a disproportionate increase in speed required. But limits are set by the Verdichterradmaterials, respectively, it must be changed to a material with better mechanical properties. Such materials are much more expensive. Compared to this solution, the injection of air shows cost advantages, since an existing compressor stage to achieve higher pressure conditions is improved and the costly material change can be avoided in the compressor.
Aus "Centrifugal Compressor Flow Range Extension Using Diffuser Flow Control", (
Beim Coanda-Effekt (beschrieben in
Die Druckluftdüsen sind in der den Strömungskanal begrenzenden Gehäusewand angeordnet und am Verdichtergehäuse festgeschraubt. Sie lassen sich in den Öffnungen bewegen, so dass die Einblasrichtung verändert werden kann. Die Düsen sind über eine Rohrleitung mit einer externen Druckluftversorgung verbunden.The compressed air nozzles are arranged in the housing wall defining the flow channel and screwed tight to the compressor housing. They can be moved in the openings, so that the blowing direction can be changed. The nozzles are connected via a pipe to an external compressed air supply.
Die
Aufgabe der Erfindung ist es, eine vereinfachte, kostengünstige Vorrichtung zum Einblasen von Luft in den Strömungskanal eines Radialverdichters zu schaffen, welche insbesondere mit geringem Aufwand montiert werden kann und die eine hohe Zuverlässigkeit im Betrieb aufweist.The object of the invention is to provide a simplified, inexpensive device for blowing air into the flow channel of a centrifugal compressor, which can be mounted in particular with little effort and has a high reliability in operation.
Diese Aufgabe löst eine Vorrichtung zum Einblasen von Luft in den Strömungskanal eines Radialverdichters mit den Merkmalen des Patentanspruchs 1.This object is achieved by a device for blowing air into the flow channel of a centrifugal compressor with the features of patent claim 1.
Bei der erfindungsgemässen Vorrichtung sind die Düsen als Einblasöffnungen in der den Strömungskanal begrenzenden Gehäusewand geformt. Die Einblasöffnungen sind direkt mittels stromab des Diffusors dem Sammelhohlraum entnommener Luft gespiesen. Diese Luft weist gegenüber der Strömung im Strömungskanal vor dem Diffusor einen erhöhten Druck auf.In the device according to the invention, the nozzles are shaped as injection openings in the housing wall delimiting the flow channel. The injection openings are fed directly by means of air taken from the collecting cavity downstream of the diffuser. This air has compared to the flow in the flow channel in front of the diffuser on an increased pressure.
Dadurch ergibt sich ein passives, dynamisches Stabilisierungssystem einer Verdichterstufe im Bereich hoher Druckverhältnisse, welches ohne zusätzliche Regel- oder Stellglieder auskommt.This results in a passive, dynamic stabilization system of a compressor stage in the range of high pressure conditions, which manages without additional control or actuators.
Eine vorteilhafte Ausführungsform der erfindungsgemässen Vorrichtung zum Einblasen von Luft in den Strömungskanal lässt sich einfach realisieren, indem die gegossenen Verdichtergehäuseteile direkt mit den entsprechenden Öffnungen versehen werden. Es sind keine zusätzlichen Düsenelemente oder Druckluftanschlüsse notwendig.An advantageous embodiment of the inventive device for blowing air into the flow channel can be easily realized by the cast compressor housing parts are provided directly with the corresponding openings. There are no additional nozzle elements or compressed air connections necessary.
Die Verteilung der Druckluft auf allenfalls mehrere Einblasöffnungen erfolgt über einen zumindest teilweise ringförmig ausgebildeten, als Hohlraum in das Verdichtergehäuse integrierten Luftkanal.The distribution of compressed air on at most several injection openings via an at least partially annular formed, integrated as a cavity in the compressor housing air duct.
Nachfolgend wird anhand der Zeichnungen die erfindungsgemässe Vorrichtung zum Einblasen von Luft in den Strömungskanal eines Radialverdichters genauer erläutert. Hierbei zeigt
- Fig. 1
- einen Schnitt durch einen Radialverdichter mit einer erfindungsgemässen Vorrichtung zum Einblasen von Luft in den Strömungskanal,
- Fig. 2
- einen vergrössert dargestellten Ausschnitt der erfindungsgemässen Vorrichtung nach
Fig. 1 mit einem aufgesetzten Düsenelement, und - Fig. 3
- einen vergrössert dargestellten Ausschnitt der erfindungsgemässen Vorrichtung nach
Fig. 1 mit einem materialschlüssig integrierten Düsenelement.
- Fig. 1
- a section through a radial compressor with an inventive device for blowing air into the flow channel,
- Fig. 2
- an enlarged section of the inventive device according to
Fig. 1 with an attached nozzle element, and - Fig. 3
- an enlarged section of the inventive device according to
Fig. 1 with a material integrated nozzle element.
Die erfindungsgemässe Vorrichtung zum Einblasen von Luft in den Strömungskanal umfasst einen Rückführungs-Luftkanal 44, welcher vom Sammelhohlraum 43 stromab der Diffusorleitschaufeln 21 in den Strömungskanal 42 zwischen den Laufschaufeln 11 des Verdichterrades und den Leitschaufeln 21 des Diffusors führt.The device according to the invention for injecting air into the flow channel comprises a
Wie in
Die Strömung im Strömungskanal weist beim Austritt aus dem Bereich der Laufschaufeln des Verdichterrades eine starke tangentiale Komponente auf. Der Coanda-Effekt sorgt dafür, dass beim Einblasen der Luft in den Strömungskanal keine starken Verwirbelungen und Querströmungen entstehen. Stattdessen bleibt die ebenfalls in tangentialer Richtung in den Strömungskanal eingeblasene Luft an der Rundung der Einblasöffnung 51 haften und wird im Randbereich des Strömungskanals in Strömungsrichtung in die Strömung eingeführt, wie dies in
Die Einblasung in den Strömungskanal erfolgt passiv, das heisst ohne Regel- oder Stellglieder. Aufgrund des höheren Drucks im Sammelhohlraum 43 gegenüber dem Strömungskanal 42 im Bereich zwischen den Laufschaufeln 11 des Verdichterrades und den Leitschaufeln 21 des Diffusors ergibt sich eine Ausgleichsströmung.The injection into the flow channel is passive, that is without control or actuators. Due to the higher pressure in the collecting
Entlang dem Umfang des Strömungskanals, also auf gleicher radialer Höhe bezüglich der Welle des Turboladers, können mehrere Einblasöffnungen 51 vorgesehen sein. Diese können alle mit einem einzigen, ringförmig oder zumindest teilweise ringförmig ausgebildeten Luftkanal 44 verbunden sein. Ebenso können in Umfangsrichtung entlang dem Sammelhohlraum 43 mehrere Entnahmeöffnungen 52 angeordnet sein. Anstelle von einem, ringförmigen Luftkanal 44 können mehrere, durch radial verlaufende Trennwände unterteilte Teilluftkanäle vorhanden sein, welche jeweils eine oder mehrere Einblasöffnungen 51 mit Luft zum Einblasen versorgen.Along the circumference of the flow channel, ie at the same radial height with respect to the shaft of the turbocharger, a plurality of
Die Öffnungen der erfindungsgemässen Vorrichtung können bereits bei der Herstellung der Verdichtergehäuseteile in diese eingelassen werden. Dies kann direkt beim Giessen der Verdichtergehäuseteile erfolgen, indem entweder vorfabrizierte Düsenelemente 62 in die Gehäusewand eingegossen und materialschlüssig mit der Gehäusewand verbunden werden, oder indem die spezielle Kontur der Einblasöffnungen bereits in der Gussform integriert ist. Bei den vorfabrizierten Düsenelementen 62 wird ein Material verwendet, welches sich beim Giessen mit dem Stahl der Gehäusewand verbindet, ohne selber zu verschmelzen. Alternativ können die Einlass- und die Einblasöffnungen auch zu einem späteren Zeitpunkt in die Verdichtergehäusewände eingebracht werden.The openings of the device according to the invention can already be embedded in these during the production of the compressor housing parts. This can be done directly when casting the compressor housing parts by either
Es können auch Düsenelemente 61 vorgesehen sein, welche form- oder kraftschlüssig mit den Verdichtergehäusewand 31 verbunden werden. Dies ermöglicht beispielsweise das Nachrüsten bereits bestehender Turbolader mit der erfindungsgemässen Vorrichtung zum Einblasen von Luft in den Strömungskanal.It can also be provided
Zur Schubentlastung im Bereich der Verdichterradrückwand oder als Sperrluft zur Ölabdichtung der Lager mittels Überdruck kann dem Verdichter im Bereich stromab der Laufschaufeln des Verdichterrades Luft entnommen werden. Diese sogenannte Leckageströmung 53 kann wiederum eine destabilisierende Wirkung auf die Verdichterströmung haben, wodurch sich die Pumpgrenze zu höheren Volumenströmen verschiebt, was zu einer unerwünschten Verminderung der nutzbaren Kennfeldbreite führt. Mittels dem erfindungsgemässen Einblasen kann der Verlauf der Pumpgrenze wieder auf den Verlauf ohne Leckageströmung 53 zurückversetzt werden.For relieving the thrust in the region of the compressor wheel back wall or as sealing air for oil sealing of the bearings by means of overpressure, air can be taken from the compressor in the region downstream of the rotor blades of the compressor wheel. This so-called
- 1010
- Verdichterrad-NabeCompressor wheel hub
- 1111
- Verdichterrad-SchaufelnCompressor blades
- 2020
- Diffusor-WandDiffuser wall
- 2121
- Diffusor-LeitschaufelDiffuser vane
- 3131
- Innere Verdichtergehäusewand, EinsatzwandInner compressor housing wall, insert wall
- 3232
- Äussere Verdichtergehäusewand, SchneckengehäuseExternal compressor housing wall, screw housing
- 3333
- Trennwandpartition wall
- 4141
- Strömungskanal, AnsaugbereichFlow channel, intake area
- 4242
- Strömungskanal, DiffusorbereichFlow channel, diffuser area
- 4343
- Sammelhohlraum, SchneckengehäuseCollective cavity, screw housing
- 4444
- Luftkanal, HohlraumAir duct, cavity
- 5151
- Einblasöffnunginflation opening
- 5252
- Entnahmeöffnungremoval opening
- 5353
- LeckströmungsöffnungLeakage opening
- 6161
- Düsenelement, aufgesetztNozzle element, mounted
- 6262
- Düsenelement, in Gehäusewand integriertNozzle element integrated in housing wall
Claims (7)
- Device for injecting air into the flow passage (42) of a radial compressor, which flow passage guides a main flow between a compressor wheel (10, 11) and a collecting chamber (43), which device comprises a discrete number of injection orifices (51) which are arranged in a manner in which they are distributed along the circumference and tangentially oriented, which injection orifices are provided with a Coanda structure and formed in the form of a nozzle, and by means of which air can be injected in the tangential direction into the flow passage (42) between rotor blades (11) of the compressor wheel and stator blades (21) of a diffuser, wherein at least one bleed orifice (52) is let in in the compressor casing wall (32) in the region of the collecting chamber (43), and the injection orifices (51) are connected via a passage (44) to the at least one bleed orifice (52).
- Device according to Claim 1, characterized in that the passage between the at least one injection orifice (51) and the at least one bleed orifice (52) is formed as a cavity (44) which extends in the circumferential direction and is formed at least partially in annular fashion.
- Device according to Claim 2, characterized in that the cavity (44) is defined by compressor casing walls (31, 32, 33).
- Device according to one of the preceding claims, characterized in that the at least one injection orifice (51) is let into the compressor casing wall (31) which defines the flow passage, and is formed by the compressor casing wall (31) which defines the flow passage.
- Device according to one of Claims 1 to 3, characterized in that the at least one injection orifice (51) is formed by a one-piece or multi-piece nozzle element (61) which is arranged in an orifice of the compressor casing wall (31) and connected to the compressor casing wall.
- Device according to one of Claims 1 to 3, characterized in that the at least one injection orifice (51) is formed by a one-piece or multi-piece nozzle element (62) which is integrated in the compressor casing wall (31) in a materially flush manner.
- Exhaust gas turbocharger, which comprises a radial compressor with a device for injecting air into the flow passage (42) of the radial compressor, according to one of the preceding claims.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06705411.4A EP1866545B1 (en) | 2005-04-04 | 2006-03-22 | Flow stabilization system for centrifugal compressor |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05405278A EP1710442A1 (en) | 2005-04-04 | 2005-04-04 | Flow stabilisation system for radial compressor |
EP06705411.4A EP1866545B1 (en) | 2005-04-04 | 2006-03-22 | Flow stabilization system for centrifugal compressor |
PCT/CH2006/000171 WO2006105678A1 (en) | 2005-04-04 | 2006-03-22 | Flow stabilization system for centrifugal compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1866545A1 EP1866545A1 (en) | 2007-12-19 |
EP1866545B1 true EP1866545B1 (en) | 2015-06-17 |
Family
ID=35005737
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
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EP05405278A Withdrawn EP1710442A1 (en) | 2005-04-04 | 2005-04-04 | Flow stabilisation system for radial compressor |
EP06705411.4A Not-in-force EP1866545B1 (en) | 2005-04-04 | 2006-03-22 | Flow stabilization system for centrifugal compressor |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
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EP05405278A Withdrawn EP1710442A1 (en) | 2005-04-04 | 2005-04-04 | Flow stabilisation system for radial compressor |
Country Status (7)
Country | Link |
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US (1) | US7648331B2 (en) |
EP (2) | EP1710442A1 (en) |
JP (1) | JP4819872B2 (en) |
KR (1) | KR101265814B1 (en) |
CN (1) | CN100529427C (en) |
RU (1) | RU2389907C2 (en) |
WO (1) | WO2006105678A1 (en) |
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DE102008015207A1 (en) * | 2008-03-20 | 2009-09-24 | Rolls-Royce Deutschland Ltd & Co Kg | Fluid injector nozzle |
DE102009021968A1 (en) * | 2009-05-19 | 2010-12-16 | Man Diesel & Turbo Se | Compressor for a turbocharger and turbocharger equipped therewith |
US9567942B1 (en) * | 2010-12-02 | 2017-02-14 | Concepts Nrec, Llc | Centrifugal turbomachines having extended performance ranges |
FR2975451B1 (en) * | 2011-05-16 | 2016-07-01 | Turbomeca | PROCESS FOR BLOWING IN GAS TURBINE DIFFUSER AND CORRESPONDING DIFFUSER |
US8596035B2 (en) | 2011-06-29 | 2013-12-03 | Opra Technologies B.V. | Apparatus and method for reducing air mass flow for extended range low emissions combustion for single shaft gas turbines |
JP5167403B1 (en) * | 2011-12-08 | 2013-03-21 | 三菱重工業株式会社 | Centrifugal fluid machine |
WO2014062372A1 (en) * | 2012-10-15 | 2014-04-24 | Borgwarner Inc. | Exhaust-gas turbocharger |
JP2014152637A (en) * | 2013-02-05 | 2014-08-25 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor |
JP6367660B2 (en) | 2014-09-19 | 2018-08-01 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor |
JP7047468B2 (en) * | 2018-03-05 | 2022-04-05 | いすゞ自動車株式会社 | Turbo turbocharger, turbocharger system and turbocharger system supercharging method |
DE102018115446A1 (en) * | 2018-06-27 | 2020-01-02 | Ihi Charging Systems International Gmbh | turbocharger |
US11143201B2 (en) * | 2019-03-15 | 2021-10-12 | Pratt & Whitney Canada Corp. | Impeller tip cavity |
CN111963490B (en) * | 2020-08-07 | 2022-06-21 | 中国北方发动机研究所(天津) | Vibration suppression structure of vane diffuser of turbocharger |
US11268536B1 (en) | 2020-09-08 | 2022-03-08 | Pratt & Whitney Canada Corp. | Impeller exducer cavity with flow recirculation |
CN114321014A (en) * | 2021-12-24 | 2022-04-12 | 中国科学院工程热物理研究所 | Local self-circulation flow control structure of radial diffuser of centrifugal compressor |
DE102022120820A1 (en) | 2022-08-17 | 2024-02-22 | Rolls-Royce Solutions GmbH | Compressor housing, radial compressor with such a compressor housing, radial compressor arrangement, exhaust gas turbocharger and internal combustion engine |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR963540A (en) * | 1950-07-17 | |||
US2052869A (en) | 1934-10-08 | 1936-09-01 | Coanda Henri | Device for deflecting a stream of elastic fluid projected into an elastic fluid |
CH204331A (en) * | 1937-02-24 | 1939-04-30 | Rheinmetall Borsig Ag | Device to prevent jet separation in turbo compressors. |
US2656096A (en) * | 1946-01-04 | 1953-10-20 | Rateau Soc | Centrifugal pump and compressor |
DE1096536B (en) * | 1953-08-17 | 1961-01-05 | Rheinische Maschinen Und App G | Centrifugal compressor, from the impeller of which the conveying medium enters a guide device concentrically surrounding the impeller at supersonic speed |
GB775784A (en) * | 1954-10-14 | 1957-05-29 | Blackburn & Gen Aircraft Ltd | Improvements in or relating to turbine engines |
US4131389A (en) * | 1975-11-28 | 1978-12-26 | The Garrett Corporation | Centrifugal compressor with improved range |
DE3443324C1 (en) * | 1984-11-28 | 1986-08-07 | M.A.N.-B & W Diesel GmbH, 8900 Augsburg | Internal combustion engine with supercharging |
DE3705307A1 (en) * | 1987-02-19 | 1988-09-01 | Kloeckner Humboldt Deutz Ag | RADIAL COMPRESSORS |
DE4334466A1 (en) * | 1993-10-09 | 1995-04-13 | Abb Management Ag | Exhaust gas turbocharger |
US6168375B1 (en) * | 1998-10-01 | 2001-01-02 | Alliedsignal Inc. | Spring-loaded vaned diffuser |
US6357374B1 (en) * | 2000-07-21 | 2002-03-19 | Cortana Corporation | Method and apparatus for increasing the effectiveness and efficiency of multiple boundary layer control techniques |
-
2005
- 2005-04-04 EP EP05405278A patent/EP1710442A1/en not_active Withdrawn
-
2006
- 2006-03-22 WO PCT/CH2006/000171 patent/WO2006105678A1/en active Application Filing
- 2006-03-22 EP EP06705411.4A patent/EP1866545B1/en not_active Not-in-force
- 2006-03-22 KR KR1020077025533A patent/KR101265814B1/en not_active IP Right Cessation
- 2006-03-22 JP JP2008504596A patent/JP4819872B2/en not_active Expired - Fee Related
- 2006-03-22 CN CNB2006800178281A patent/CN100529427C/en not_active Expired - Fee Related
- 2006-03-22 RU RU2007140869/06A patent/RU2389907C2/en not_active IP Right Cessation
-
2007
- 2007-10-02 US US11/865,837 patent/US7648331B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US20080038112A1 (en) | 2008-02-14 |
WO2006105678A1 (en) | 2006-10-12 |
CN101180468A (en) | 2008-05-14 |
JP4819872B2 (en) | 2011-11-24 |
RU2007140869A (en) | 2009-05-20 |
US7648331B2 (en) | 2010-01-19 |
KR20070113323A (en) | 2007-11-28 |
KR101265814B1 (en) | 2013-05-20 |
JP2008534858A (en) | 2008-08-28 |
EP1710442A1 (en) | 2006-10-11 |
RU2389907C2 (en) | 2010-05-20 |
CN100529427C (en) | 2009-08-19 |
EP1866545A1 (en) | 2007-12-19 |
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