EP0601227A1 - Stabilizing device for the increase of the surge margin of a compressor - Google Patents

Stabilizing device for the increase of the surge margin of a compressor Download PDF

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Publication number
EP0601227A1
EP0601227A1 EP92120867A EP92120867A EP0601227A1 EP 0601227 A1 EP0601227 A1 EP 0601227A1 EP 92120867 A EP92120867 A EP 92120867A EP 92120867 A EP92120867 A EP 92120867A EP 0601227 A1 EP0601227 A1 EP 0601227A1
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EP
European Patent Office
Prior art keywords
compressor
ring
impeller
recess
housing
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
EP92120867A
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German (de)
French (fr)
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EP0601227B1 (en
Inventor
Klaus Dr.-Ing. Heinrich
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.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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.)
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Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to EP92120867A priority Critical patent/EP0601227B1/en
Priority to DE59208865T priority patent/DE59208865D1/en
Priority to US08/153,427 priority patent/US5375974A/en
Priority to KR1019930024777A priority patent/KR940015291A/en
Priority to CZ932503A priority patent/CZ283127B6/en
Priority to PL93301303A priority patent/PL172608B1/en
Priority to JP5305071A priority patent/JPH06235398A/en
Priority to CN93120889A priority patent/CN1034605C/en
Publication of EP0601227A1 publication Critical patent/EP0601227A1/en
Application granted granted Critical
Publication of EP0601227B1 publication Critical patent/EP0601227B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports

Definitions

  • the invention relates to a stabilization device for expanding a characteristic map of a compressor.
  • the aim is to achieve monotonically falling characteristic curves with no hysteresis as the flow increases, in order to achieve high reliability in part-load operation.
  • Such continuous characteristics are called stable.
  • stable characteristics are more difficult to achieve the greater the pressure ratio at the design point. That's why you try to generate the desired stable characteristic curves by means of additional stabilizing devices.
  • the stabilization device described for example in the patent specification CH 675 279 consists of a recess in the housing of a radial compressor, a stabilization ring being integrated into this recess.
  • the recess or the stabilizing ring are arranged in front of the impeller and outside the main flow.
  • Stabilizing blades are present on the outer circumference of the stabilizing ring and are anchored to the inner contour of the recess.
  • the disadvantage of this solution is the complex design of the housing, the ring and the stabilizing blades.
  • the already high vibration load on the rotor blades in the entry area is increased by the stabilizing device.
  • This device consists of a ring fixedly connected to the blades, a relatively large radial recirculation channel being arranged between the ring and the housing of the compressor.
  • a recirculation flow is made possible, which contributes to the stabilization of the map.
  • the ring supports the blade leading edges in both the radial and tangential directions and thereby reduces the blade vibrations.
  • the disadvantage of this solution is the necessity of the relatively large recirculation channel and the fact that with some radial compressors an undesirably strong recirculation occurs.
  • the invention tries to avoid all these disadvantages. It is based on the task of a compressor in the impeller inlet area to prevent the formation of the harmful gap flow from one blade side to the other and thus to expand the compressor map by stabilizing the flow and at the same time to eliminate the vibration problems in the impeller inlet area.
  • the stabilization device consists of a ring fixedly attached to the rotor blades and a recess in the housing of the compressor in the form of a rotationally symmetrical groove, the ring being attached in the inlet area of the impeller such that the ring rotates when the impeller rotates the recess is movable, with only a usual close play between the ring and the wall of the housing.
  • the advantages of the invention can be seen, inter alia, in the fact that no vortices or only vortices occur to a reduced extent in the inlet part of the impeller.
  • the efficiency of the compressor is increased and the stable range of the compressor characteristic is widened.
  • the blades support the blades in the tangential and radial directions, so that the vibration load is reduced. Since the ring is only limited to the inlet part of the impeller and the radius there is smaller than at the impeller outlet, the centrifugal force is relatively small and therefore manageable.
  • FIG. 1 An embodiment of the invention is shown using a radial compressor.
  • the single figure shows a partial meridian section of the compressor with the stabilization device. Only the elements essential for understanding the invention are shown.
  • the direction of flow of the working fluid is indicated by an arrow.
  • part of a radial compressor is shown with the stabilization device according to the invention.
  • the compressor consists of the housing 4 and the impeller 3.
  • the impeller 3 is equipped with a ring 1 fixed to the blades 2 in the form of a short cover plate. This cover plate is only limited to the inlet part of the impeller 3.
  • a recess 5 in the form of a rotationally symmetrical groove is present in the housing 4 of the compressor.
  • the dimensions of the recess 5 are matched to the dimensions of the ring 1 such that the ring 1 is easily movable in the recess 5 when the impeller 3 rotates, but only the usual close play exists between the ring 1 and the wall of the housing 4, which z. B. is also present between the upper edges of the blades 2 and the wall of the housing 4.
  • the ring 1 supports the blade leading edges in the radial and tangential directions. The result is that the blade vibration amplitudes are greatly reduced and the mechanical blade load is reduced. Since the ring 1 is only limited to the inlet part of the impeller 3, where the radius is significantly smaller than at the impeller outlet, the centrifugal force is also significantly smaller and therefore manageable. A destruction of the ring 1 due to excessive centrifugal force thus does not take place.
  • the ring 1 rotating in the recess 5 with the impeller 3 prevents the formation of the gap flow over the outer edges of the blades in the impeller region in which the gap flow would contribute to the formation of a harmful vortex.
  • the vortex does not arise at all or only in a reduced scope. This increases the efficiency of the compressor and widens the stable range of the compressor characteristic.

Abstract

In a stablising device for the increase of the surge margin of a compressor, which device consists of a ring (1), mounted fixedly on the vanes (2) of the impeller (3), and a recess (5) in the housing (4) of the compressor in the form of a rotationally symmetrical groove, the ring (1) is restricted to the entry region of the impeller (3) and is mounted there in such a way that it is movable in the recess (5) when the impeller (3) is rotating, there being only the usual narrow clearance between the ring (1) and the wall of the housing (4). This prevents the formation of a gap flow from the vane side with high pressure to that with low pressure, which leads to an increase in the degree of efficiency of the compressor and to the broadening of the compressor characteristic. At the same time, the vibration loading of the vanes is reduced. <IMAGE>

Description

Technisches GebietTechnical field

Die Erfindung betrifft eine Stabilisierungseinrichtung zur Kennfelderweiterung eines Verdichters gemäss Oberbegriff des Anspruches 1.The invention relates to a stabilization device for expanding a characteristic map of a compressor.

Stand der TechnikState of the art

Es ist bekannt, dass sich bei Rotation eines Verdichterrades im Spalt zwischen den rotierenden Aussenkanten der Laufschaufein und dem ruhenden Gehäuse eine Spaltströmung von der Schaufelseite mit hohem Druck zu der mit niedrigem Druck einstellt. Diese Spaltströmung kann zusammen mit anderen Strömungsvorgängen im Eintrittsteil des Radialrades zu einem Wirbel führen. Durch diesen Wirbel wird der Wirkungsgrad des Verdichters verringert, und der stabile Bereich der Verdichterkennlinie wird schmaler.It is known that when a compressor wheel rotates in the gap between the rotating outer edges of the rotor blade and the stationary housing, a gap flow occurs from the blade side at high pressure to that at low pressure. This gap flow together with other flow processes can lead to a vortex in the inlet part of the radial wheel. This vortex reduces the efficiency of the compressor and the stable area of the compressor characteristic curve becomes narrower.

Bei Verwendung von Turboverdichtern wird angestrebt, mit wachsendem Durchfluss monoton fallende Kennlinien ohne Hysterese zu erzielen, um eine hohe Zuverlässigkeit bei Teillastbetrieb zu erreichen. Solche kontinuierliche Kennlinien werden als stabil bezeichnet. Bei Teillast sind jedoch stabile Kennlinien um so schwerer zu erzielen, je grösser das Druckverhältnis im Auslegungspunkt ist. Deshalb versucht man mittels zusätzlicher Stabilisierungseinrichtungen die gewünschten stabilen Kennlinien zu erzeugen.When using turbocompressors, the aim is to achieve monotonically falling characteristic curves with no hysteresis as the flow increases, in order to achieve high reliability in part-load operation. Such continuous characteristics are called stable. At partial load, however, stable characteristics are more difficult to achieve the greater the pressure ratio at the design point. That's why you try to generate the desired stable characteristic curves by means of additional stabilizing devices.

Die beispielsweise in der Patentschrift CH 675 279 beschriebene Stabilisierungseinrichtung besteht aus einer Ausnehmung im Gehäuse eines Radialverdichters, wobei in diese Ausnehmung ein Stabilisierungsring intergriert ist. Die Ausnehmung bzw. der Stabilisierungsring sind dabei vor dem Laufrad und ausserhalb der Hauptströmung angeordnet. Am Aussenumfang des Stabilisierungsringes sind Stabilisierungsschaufeln vorhanden, die an der Innenkontur der Ausnehmung verankert sind. Der Nachteil dieser Lösung besteht in der aufwendigen konstruktiven Gestaltung des Gehäuses, des Ringes und der Stabilisierungschaufeln. Ausserdem wird die ohnehin schon grosse Schwingungsbelastung der Laufschaufeln im Eintrittsbereich durch die Stabilisierungsvorrichtung noch verstärkt.The stabilization device described for example in the patent specification CH 675 279 consists of a recess in the housing of a radial compressor, a stabilization ring being integrated into this recess. The recess or the stabilizing ring are arranged in front of the impeller and outside the main flow. Stabilizing blades are present on the outer circumference of the stabilizing ring and are anchored to the inner contour of the recess. The disadvantage of this solution is the complex design of the housing, the ring and the stabilizing blades. In addition, the already high vibration load on the rotor blades in the entry area is increased by the stabilizing device.

Der Anmelderin ist eine Stabilisierungseinrichtung bekannt, bei der die eben genannten Nachteile reduziert werden. Diese Einrichtung besteht aus einem fest mit den Laufschaufeln verbundenen Ring, wobei zwischen dem Ring und dem Gehäuse des Verdichters ein relativ grosser radialer Rezirkulationskanal angeordnet ist. Bei starker Drosselung des Verdichters wird dort eine Rezirkulationsströmung ermöglicht, welche zur Kennfeldstabilisierung beiträgt. Der Ring stützt die Schaufeleintrittskanten sowohl in radialer als auch in tangentialer Richtung ab und reduziert dadurch die Schaufelschwingungen. Der Nachteil dieser Lösung besteht in der Notwendigkeit des relativ grossen Rezirkulationskanales und der Tatsache, dass bei manchen Radialverdichtern eine unerwünscht starke Rezirkulation eintritt.The applicant is aware of a stabilization device in which the disadvantages just mentioned are reduced. This device consists of a ring fixedly connected to the blades, a relatively large radial recirculation channel being arranged between the ring and the housing of the compressor. When the compressor is severely throttled, a recirculation flow is made possible, which contributes to the stabilization of the map. The ring supports the blade leading edges in both the radial and tangential directions and thereby reduces the blade vibrations. The disadvantage of this solution is the necessity of the relatively large recirculation channel and the fact that with some radial compressors an undesirably strong recirculation occurs.

Darstellung der ErfindungPresentation of the invention

Die Erfindung versucht, all diese Nachteile zu vermeiden. Ihr liegt die Aufgabe zugrunde, bei einem Verdichter im Laufradeintrittsbereich die Ausbildung des schädlichen Spaltstromes von einer Schaufelseite zur anderen zu verhindern und damit durch Stabilisierung der Strömung das Verdichterkennfeld zu erweitern und gleichzeitig die Schwingungsprobleme im Laufradeintrittsbereich zu beseitigen.The invention tries to avoid all these disadvantages. It is based on the task of a compressor in the impeller inlet area to prevent the formation of the harmful gap flow from one blade side to the other and thus to expand the compressor map by stabilizing the flow and at the same time to eliminate the vibration problems in the impeller inlet area.

Erfindungsgemäss wird dies dadurch erreicht, dass die Stabilisierungseinrichtung aus einem fest auf den Laufschaufeln angebrachten Ring und einer Ausnehmung im Gehäuse des Verdichters in Form einer rotationssymmetrischen Nut besteht, wobei der Ring im Eintrittsbereich des Laufrades so angebracht ist, dass der Ring bei Rotation des Laufrades in der Ausnehmung beweglich ist, wobei zwischen dem Ring und der Wand des Gehäuses nur ein übliches enges Spiel besteht.According to the invention, this is achieved in that the stabilization device consists of a ring fixedly attached to the rotor blades and a recess in the housing of the compressor in the form of a rotationally symmetrical groove, the ring being attached in the inlet area of the impeller such that the ring rotates when the impeller rotates the recess is movable, with only a usual close play between the ring and the wall of the housing.

Die Vorteile der Erfindung sind unter anderem darin zu sehen, dass im Eintrittsteil des Laufrades keine Wirbel bzw. nur noch Wirbel in verringertem Umfang entstehen. Das führt dazu, dass der Wirkungsgrad des Verdichters erhöht wird und der stabile Bereich der Verdichterkennlinie verbreitert wird. Gleichzeitig werden durch den Ring die Schaufeln in tangentialer und radialer Richtung abgestützt, so dass die Schwingungsbelastung zurückgeht. Da der Ring nur auf den Eintrittsteil des Laufrades beschränkt ist und dort der Radius kleiner als am Laufradaustritt ist, ist die Fliehkraftbeanspruchung relativ klein und dadurch beherrschbar.The advantages of the invention can be seen, inter alia, in the fact that no vortices or only vortices occur to a reduced extent in the inlet part of the impeller. As a result, the efficiency of the compressor is increased and the stable range of the compressor characteristic is widened. At the same time, the blades support the blades in the tangential and radial directions, so that the vibration load is reduced. Since the ring is only limited to the inlet part of the impeller and the radius there is smaller than at the impeller outlet, the centrifugal force is relatively small and therefore manageable.

Kurze Beschreibung der ZeichnungBrief description of the drawing

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung anhand eines Radialverdichters dargestellt. Die einzige Figur zeigt einen Teilmeridianschnitt des Verdichters mit der Stabilisierungseinrichtung. Es sind nur die für das Verständnis der Erfindung wesentlichen Elemente gezeigt. Die Strömungsrichtung des Arbeitsmittels ist mit einem Pfeil bezeichnet.In the drawing, an embodiment of the invention is shown using a radial compressor. The single figure shows a partial meridian section of the compressor with the stabilization device. Only the elements essential for understanding the invention are shown. The direction of flow of the working fluid is indicated by an arrow.

Weg zur Ausführung der ErfindungWay of carrying out the invention

In der Figur ist ein Teil eines Radialverdichters mit der erfindungsgemässen Stabilisierungseinrichtung dargestellt.In the figure, part of a radial compressor is shown with the stabilization device according to the invention.

Der Verdichter besteht aus dem Gehäuse 4 und dem Laufrad 3. Das Laufrad 3 ist mit einem fest mit den Laufschaufeln 2 verbundenen Ring 1 in Form einer kurzen Deckscheibe ausgerüstet. Diese Deckscheibe ist nur auf den Eintrittsteil des Laufrades 3 beschränkt. Im Gehäuse 4 des Verdichters ist eine Ausnehmung 5 in Form einer rotationssymmetrischen Nut vorhanden.The compressor consists of the housing 4 and the impeller 3. The impeller 3 is equipped with a ring 1 fixed to the blades 2 in the form of a short cover plate. This cover plate is only limited to the inlet part of the impeller 3. A recess 5 in the form of a rotationally symmetrical groove is present in the housing 4 of the compressor.

Die Abmasse der Ausnehmung 5 sind auf die Abmasse des Ringes 1 so abgestimmt, dass der Ring 1 bei Rotation des Laufrades 3 in der Ausnehmung 5 gut beweglich ist, aber zwischen dem Ring 1 und der Wand des Gehäuses 4 nur das übliche enge Spiel besteht, welches z. B. auch zwischen den Oberkanten der Laufschaufeln 2 und der Wand des Gehäuses 4 vorhanden ist.The dimensions of the recess 5 are matched to the dimensions of the ring 1 such that the ring 1 is easily movable in the recess 5 when the impeller 3 rotates, but only the usual close play exists between the ring 1 and the wall of the housing 4, which z. B. is also present between the upper edges of the blades 2 and the wall of the housing 4.

Der Ring 1 stützt die Schaufeleintrittskanten in radialer und tangentialer Richtung ab. Das führt dazu, dass die Schaufelschwingungsamplituden stark reduziert werden und die mechanische Schaufelbelastung sinkt. Da der Ring 1 nur auf den Eintrittsteil des Laufrades 3 beschränkt ist, wo der Radius wesentlich kleiner als am Laufradaustritt ist, ist auch die Fliehkraftbeanspruchung wesentlich kleiner und dadurch beherrschbar. Eine Zerstörung des Ringes 1 infolge zu hoher Fliehkraft findet somit nicht statt.The ring 1 supports the blade leading edges in the radial and tangential directions. The result is that the blade vibration amplitudes are greatly reduced and the mechanical blade load is reduced. Since the ring 1 is only limited to the inlet part of the impeller 3, where the radius is significantly smaller than at the impeller outlet, the centrifugal force is also significantly smaller and therefore manageable. A destruction of the ring 1 due to excessive centrifugal force thus does not take place.

Der in der Ausnehmung 5 mit dem Laufrad 3 rotierende Ring 1 verhindert die Ausbildung der Spaltströmung über die Schaufelaussenkanten in dem Laufradbereich, in welchem die Spaltströmung zur Ausbildung eines schädlichen Wirbels beitragen würde. Der Wirbel entsteht dadurch gar nicht erst bzw. nur in einem reduzierten Umfang. Dadurch wird der Wirkungsgrad des Verdichters erhöht und der stabile Bereich der Verdichterkennlinie wird verbreitert.The ring 1 rotating in the recess 5 with the impeller 3 prevents the formation of the gap flow over the outer edges of the blades in the impeller region in which the gap flow would contribute to the formation of a harmful vortex. The vortex does not arise at all or only in a reduced scope. This increases the efficiency of the compressor and widens the stable range of the compressor characteristic.

BezugszeichenlisteReference list

11
Ringring
22nd
LaufschaufelnBlades
33rd
LaufradWheel
44th
Gehäusecasing
55
AusnehmungRecess

Claims (1)

Stabilisierungseinrichtung zur Kennfelderweiterung eines Verdichters, bestehend aus einem fest auf den Laufschaufeln (2) angebrachten Ring (1) und einer Ausnehmung (5) im Gehäuse (4) des Verdichters in Form einer rotationssymmetrischen Nut, dadurch gekennzeichnet, dass der Ring (1) im Eintrittsbereich des Laufrades (3) so angebracht ist, dass der Ring (1) bei Rotation des Laufrades (3) in der Ausnehmung (5) beweglich ist, wobei zwischen dem Ring (1) und der Wand des Gehäuses (4) nur ein übliches enges Spiel besteht.Stabilizing device for expanding the characteristic map of a compressor, consisting of a ring (1) fixed to the blades (2) and a recess (5) in the housing (4) of the compressor in the form of a rotationally symmetrical groove, characterized in that the ring (1) in the Entry area of the impeller (3) is mounted so that the ring (1) is movable in the recess (5) when the impeller (3) rotates, only a conventional one between the ring (1) and the wall of the housing (4) tight game exists.
EP92120867A 1992-12-08 1992-12-08 Stabilizing device for the increase of the surge margin of a compressor Expired - Lifetime EP0601227B1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP92120867A EP0601227B1 (en) 1992-12-08 1992-12-08 Stabilizing device for the increase of the surge margin of a compressor
DE59208865T DE59208865D1 (en) 1992-12-08 1992-12-08 Stabilizing device for expanding the map of a compressor
US08/153,427 US5375974A (en) 1992-12-08 1993-11-16 Stabilizing device for extending the characteristic diagram of a compressor
KR1019930024777A KR940015291A (en) 1992-12-08 1993-11-19 Stabilizer for Expansion of Compressor Characteristics
CZ932503A CZ283127B6 (en) 1992-12-08 1993-11-22 Stabilizing device for enlarging characteristic field of a compressor
PL93301303A PL172608B1 (en) 1992-12-08 1993-12-03 Stabilizing device for widening the characteristic curve field of a compressor
JP5305071A JPH06235398A (en) 1992-12-08 1993-12-06 Stabilizer for expanding characteristic diagram of compressor
CN93120889A CN1034605C (en) 1992-12-08 1993-12-08 Stabilizing device for extending the characteristic diagram of compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP92120867A EP0601227B1 (en) 1992-12-08 1992-12-08 Stabilizing device for the increase of the surge margin of a compressor

Publications (2)

Publication Number Publication Date
EP0601227A1 true EP0601227A1 (en) 1994-06-15
EP0601227B1 EP0601227B1 (en) 1997-09-03

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EP92120867A Expired - Lifetime EP0601227B1 (en) 1992-12-08 1992-12-08 Stabilizing device for the increase of the surge margin of a compressor

Country Status (8)

Country Link
US (1) US5375974A (en)
EP (1) EP0601227B1 (en)
JP (1) JPH06235398A (en)
KR (1) KR940015291A (en)
CN (1) CN1034605C (en)
CZ (1) CZ283127B6 (en)
DE (1) DE59208865D1 (en)
PL (1) PL172608B1 (en)

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WO2016132644A1 (en) * 2015-02-18 2016-08-25 株式会社Ihi Centrifugal compressor and supercharger
EP3530957B1 (en) * 2017-02-08 2021-05-12 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Compressor and turbocharger
WO2019087389A1 (en) 2017-11-06 2019-05-09 三菱重工エンジン＆ターボチャージャ株式会社 Centrifugal compressor and turbocharger comprising said centrifugal compressor
DE102018132978A1 (en) * 2018-12-19 2020-06-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Turbo compressor with adapted meridian contour of the blades and compressor wall
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CH675279A5 (en) * 1988-06-29 1990-09-14 Asea Brown Boveri
US5105616A (en) * 1989-12-07 1992-04-21 Sundstrand Corporation Gas turbine with split flow radial compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10223876A1 (en) * 2002-05-29 2003-12-11 Daimler Chrysler Ag Compressor, for the turbo charger of an IC motor, has a covering ring at the compressor wheel, radially around the wheel paddles, to form tunnel air flow channels between the paddles between the ring and the hub

Also Published As

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CZ283127B6 (en) 1998-01-14
PL172608B1 (en) 1997-10-31
KR940015291A (en) 1994-07-20
CN1034605C (en) 1997-04-16
JPH06235398A (en) 1994-08-23
PL301303A1 (en) 1994-06-13
DE59208865D1 (en) 1997-10-09
CN1096858A (en) 1994-12-28
CZ250393A3 (en) 1994-06-15
EP0601227B1 (en) 1997-09-03
US5375974A (en) 1994-12-27

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