EP0348674B1 - Device for extending the surge margin of a radial compressor - Google Patents

Device for extending the surge margin of a radial compressor Download PDF

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Publication number
EP0348674B1
EP0348674B1 EP89109560A EP89109560A EP0348674B1 EP 0348674 B1 EP0348674 B1 EP 0348674B1 EP 89109560 A EP89109560 A EP 89109560A EP 89109560 A EP89109560 A EP 89109560A EP 0348674 B1 EP0348674 B1 EP 0348674B1
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EP
European Patent Office
Prior art keywords
impeller
outside diameter
ratio
recess
inlet
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.)
Expired - Lifetime
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EP89109560A
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German (de)
French (fr)
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EP0348674A1 (en
Inventor
Karl-Heinz Dr. Rohne
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ABB Asea Brown Boveri Ltd
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ABB Asea Brown Boveri Ltd
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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
    • F04D29/4206—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
    • 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
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • 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

Definitions

  • the present invention relates to a device for expanding the characteristic map of a radial compressor.
  • turbocompressors be they radial or axial
  • the aim is to achieve stable characteristics that drop monotonically with increasing flow without hysteresis.
  • stable characteristics are more difficult to achieve the greater the pressure ratio at the design point.
  • practice tries to help itself to achieve the desired characteristics by means of additional stabilization devices. Due to differences in the design of the blades and in the structures of the tear-off areas during part-load operation, no clear technical solution has emerged to date, according to which a general non-slip stabilizing device could be derived.
  • a stabilizing device has become known in a radial compressor, which is characterized in that the inner housing has radial or quasi-radial bores as the sheathing of the impeller. These holes create a connection between the inflow channel and the blades, whereby they are more or less covered by the blades on the blade side. With such bores, the pumping and stability limits are shifted in the form of a map line, but this involves the loss of high efficiency, which can amount to 4 - 5 percentage points.
  • the proposed solution cannot substantially achieve the desired map expansion at low throughputs that would be necessary due to the instabilities that occur with a specific type of operation. What is also important is the fact that this minimal stabilizing effect has to be bought through a disproportionately large loss in efficiency.
  • the invention seeks to remedy this.
  • the object of the invention is to provide, in the case of radial compressors, a device for expanding the characteristic map to small throughputs by stabilizing the impeller flow in the inlet area with predeterminable accuracy.
  • the main advantage of the invention is that this device behaves neutrally as long as the radial compressor delivers the full volume flow; only when different flow structures occur, in particular at partial load, the device comes into operation and prevents the phenomenon of separation from appearing over the entire partial load range. This prevents the dreaded "pumping", which results in stable characteristics.
  • Another advantage of the invention can be seen in the fact that the device represents a simple structural arrangement that can be provided in any radial compressor, regardless of its technical specification.
  • Fig. 1 shows a partial view of a radial compressor in the area of an intended device for expanding the map when operating such a compressor.
  • the device generally effects a stabilization of the impeller flow in the inlet area during part-load operation.
  • the radial compressor consists of housing 1 and impeller 2, the above-mentioned stabilization device being provided in front of impeller 2, which in turn consists of a stabilizer opening 5, a stabilization ring 3 and a number of stabilizer blades 4.
  • the stabilizer opening 5 has the shape of an inner groove and extends in the radial direction, starting from the surface of the inlet channel 6, into the housing 1 by a certain depth; in the axial direction it extends approximately upstream by a certain length from the inflow edge of the impeller 2.
  • the stabilization ring 3 is integrated in the stabilizer opening 5, its inner circumferential surface extending into the continuation of the surface of the inlet channel 6.
  • the outer circumference of the stabilizing ring 3 is equipped with a number of blades which, in radial expansion, fill the remaining clear width of the stabilizer opening 5 and are anchored there.
  • the wall thickness of the stabilization ring 3 represents a function of the operationally required strength and stability. For fluidic considerations, the wall thickness of the stabilization ring 3 must not unnecessarily come at the expense of the height of the stabilizer blades 4. Accordingly, one is dealing with a bladed stabilizer variant, which guarantees a better effect towards eliminating a hysteresis or instability area compared to a bladed version.
  • the correct design of the stabilizer consists first of all in the correct choice of the outside diameter of the stabilizing ring 3, which is to be matched to the compressor, that is to say to the outside diameter at the impeller inlet, so that on the one hand only a little flows through the stabilizer opening 5 at the best point, so that the efficiency does not fall, on the other hand, the largest possible flow 8 must circulate at partial load.
  • the outside diameter of the stabilizing ring 3 which is to be matched to the compressor, that is to say to the outside diameter at the impeller inlet, so that on the one hand only a little flows through the stabilizer opening 5 at the best point, so that the efficiency does not fall, on the other hand, the largest possible flow 8 must circulate at partial load.
  • the partial flow 9 also receives a counter-swirl, whereby the efficiency tends to grow.
  • the exemplary embodiment mentioned here is designed such that the impeller 2 projects into the stabilizer opening 5. This has the following relevance: The further the impeller 2 protrudes into the stabilizer opening 5, the more work is transferred to the circulating air, the greater the circulating volume flow 8 and the greater the stabilizing effect of the device.
  • the width of the stabilizer blade 4 in the flow direction of the recirculating part-load flow 8 is variable, as the dashed-line stabilizer blade 4a wants to show, and can occupy the entire remaining width of the stabilizer opening 5 in this plane of expansion.
  • the widest possible stabilizer blade 4a has a channeling effect on the partial flows 8, 9 and helps to increase the stability of the device in the event of partial and overload.
  • FIG. 2 also shows a radial compressor according to FIG. 1 with a development of the stabilization ring 3 and stabilizer blade 4a for the purpose of achieving a flow improvement in the stabilizer opening 5 under partial load.
  • the stabilization ring 3a is profiled, while the stabilizer blade 4a, which has maximum axial expansion in the flow direction of the partial load flow 8, is further developed by an inflow aid 4b.
  • FIG. 2 further shows an example of the increase in the stabilizing effect of the device postulated under FIG. 1 by extending the impeller 2a in the countercurrent direction to far into the stabilizer opening 5. As can be seen in FIG. 2, it is structurally feasible to have the impeller 2a protrude into the stabilizer opening 5 as far as the stabilizing ring 3a.
  • the correct design of the stabilizer consists first of all in the correct choice of the outer diameter d of the stabilizing ring 3. It is obvious that this diameter d must be in a certain ratio to the outer diameter of the impeller inlet opening Y. to ensure the envisaged advantages of operating a radial compressor with a device for stabilizing the impeller flow in the inlet area, in particular under partial load.
  • a correct choice of the outer diameter of the stabilizing ring d is to limit it in the interval 1.02 - 1.05 to the outer diameter of the impeller inlet opening Y.
  • the sizes of the other elements of the device are derived from this choice of output, the dimensions of these elements being subsequently expressed for the sake of clarity as a ratio to the respective outer diameter of the impeller inlet opening Y.

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

Description

Die vorliegende Erfindung betrifft eine Einrichtung zur Kennfelderweiterung eines Radialverdichters gemäss Oberbegriff des Anspruchs 1.The present invention relates to a device for expanding the characteristic map of a radial compressor.

STAND DER TECHNIKSTATE OF THE ART

Bei der Verwendung von Turboverdichtern, seien sie radial oder axial, wird im Interesse einer hohen Zuverlässigkeit bei Teillastbetrieb angestrebt, stabile, mit wachsendem Durchfluss monoton fallende Kennlinien ohne Hysterese zu erzielen. Bei Teillast sind stabile Kennlinien jedoch um so schwerer zu erreichen, je grösser das Druckverhältnis im Auslegungspunkt wird. Hier versucht die Praxis sich zu behelfen, durch zusätzliche Stabilisierungseinrichtungen die gewünschten Kennlinien herbeizuführen. Bedingt durch Unterschiede in der Auslegung der Schaufeln und in den Strukturen der Abreissgebiete bei Teillastbetrieb hat sich bis heute keine klare technische Lösung herauskristallisiert, nach welcher eine allgemeine griffige Stabilisierungsvorrichtung abgeleitet werden könnte.When using turbocompressors, be they radial or axial, in the interest of high reliability in part-load operation, the aim is to achieve stable characteristics that drop monotonically with increasing flow without hysteresis. At partial load, however, stable characteristics are more difficult to achieve the greater the pressure ratio at the design point. Here, practice tries to help itself to achieve the desired characteristics by means of additional stabilization devices. Due to differences in the design of the blades and in the structures of the tear-off areas during part-load operation, no clear technical solution has emerged to date, according to which a general non-slip stabilizing device could be derived.

Zur Zeit kann somit mit naturwissenschaftlicher Genauigkeit nicht vorausgesagt werden, ob überhaupt und mit welcher Stabilisierungsvorrichtung bei einem gegebenen Verdichter eine stabile Kennlinie zu erreichen ist. Dieser unbefriedigende Zustand macht sich insbesondere bei Radialverdichtern bemerkbar.At the moment, it cannot be predicted with scientific accuracy whether a stable characteristic can be achieved at all and with which stabilization device for a given compressor. This unsatisfactory condition is particularly noticeable with radial compressors.

Aus EP-A1-0 229 519 ist in einem Radialverdichter eine Stabilisierungseinrichtung bekannt geworden, welche dadurch charakterisiert ist, dass das Innengehäuse als Ummantelung des Schaufelrades radiale oder quasiradiale Bohrungen aufweist. Diese Bohrungen stellen eine Verbindung zwischen Anströmungskanal und Beschaufelung her, wobei sie schaufelseitig von den Schaufeln mehr oder minder überdeckt werden. Mit solchen Bohrungen wird zwar die Pump- und Stabilitätsgrenze kennfeldlinienförmig verschoben, dies allerdings unter Inkaufnahme grosser Wirkungsgradeinbussen, die 4 - 5 Prozentpunkte ausmachen können. Durch die hier vorgeschlagene Lösung kann substantiell nicht jene angestrebte Kennfelderweiterung zu kleinen Durchsätzen erzielt werden, die aufgrund der bei spezifischer Betreibungsart auftretenden Instabilitäten notwendig wäre. Was überdies ins Gewicht fällt, ist die Tatsache, dass diese minimale Stabilisierungswirkung durch einen unverhältnismässig grossen Wirkungsgradverlust erkauft werden muss.From EP-A1-0 229 519 a stabilizing device has become known in a radial compressor, which is characterized in that the inner housing has radial or quasi-radial bores as the sheathing of the impeller. These holes create a connection between the inflow channel and the blades, whereby they are more or less covered by the blades on the blade side. With such bores, the pumping and stability limits are shifted in the form of a map line, but this involves the loss of high efficiency, which can amount to 4 - 5 percentage points. The proposed solution cannot substantially achieve the desired map expansion at low throughputs that would be necessary due to the instabilities that occur with a specific type of operation. What is also important is the fact that this minimal stabilizing effect has to be bought through a disproportionately large loss in efficiency.

Aus US-A-4,212,585 ist ein Zentrifugalkompressor bekannt geworden, bei welchem im Gehäuse eine freie Ausnehmung vorhanden ist, welche sich, anfangend im Bereich der Vorderkante des Laufrades, in Strömungsrichtung erstreckt. Diese Ausnehmung als solche vermag keine Stabilisierung der Strömung, falls eine solche mit dieser Vorkehrung angestrebt wurde, zu erwirken, denn innerhalb einer solchen freien Ausnehmung vermag sich einerseits keine rezirkulierende Strömung und andererseits keine Förderströmung bei Ueberlast einzustellen, womit mit dieser Vorkehrung offensichtlicht eine Kennfelderweiterung zu kleinen Durchsätzen nicht zu erreichen ist. Selbst bei einer platzmässig orientierten Verschiebung der Ausnehmung sind Ablösungserscheinungen nicht zu umgehen, denn es ist an sich bekannt, dass Ausnehmungen im Gehäuse, wie solcherart bei dieser US-Druckschrift vorgeschlagen wird, insbesondere im Teillastbereich eine Pumpwirkung, d.h. unstabile Kennlinien, bewirken, was für den Wirkungsgrad eines Verdichters immer nachteilig ist.From US-A-4,212,585 a centrifugal compressor has become known, in which there is a free recess in the housing, which extends, starting in the region of the front edge of the impeller, in the direction of flow. This recess as such cannot stabilize the flow, if such a provision was aimed at, because within such a free recess, on the one hand, no recirculating flow and, on the other hand, no delivery flow in the event of an overload can be set, which obviously means that this provision expands the map small throughputs cannot be achieved. Even with a space-oriented displacement of the recess, detachment phenomena cannot be avoided, because it is known per se that recesses in the housing, as is proposed in this US publication, cause a pumping action, ie unstable characteristic curves, in particular in the part-load range, which is what the efficiency of a compressor is always disadvantageous.

AUFGABE DER ERFINDUNGOBJECT OF THE INVENTION

Hier will die Erfindung Abhilfe schaffen. Der Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, liegt die Aufgabe zugrunde, bei Radialverdichtern eine Einrichtung zur Kennfelderweiterung zu kleinen Durchsätzen durch Stabilisierung der Laufradströmung im Eintrittsbereich mit vorausbestimmbarer Genauigkeit bereitzustellen.The invention seeks to remedy this. The object of the invention, as characterized in the claims, is to provide, in the case of radial compressors, a device for expanding the characteristic map to small throughputs by stabilizing the impeller flow in the inlet area with predeterminable accuracy.

Der wesentliche Vorteil der Erfindung ist darin zu sehen, dass sich diese Einrichtung, solange der Radialverdichter den vollen Volumenstrom fördert, neutral verhält; erst bei Eintritt unterschiedlicher Strömungsstrukturen, insbesondere bei Teillast, tritt die Einrichtung in Funktion und verhindert, dass vordergründig Ablösungserscheinung über den ganzen Teillastbereich auftreten können. Mithin wird das gefürchtete "Pumpen" unterbunden, was stabile Kennlinien ergibt. Ein weiterer Vorteil der Erfindung ist darin zu sehen, dass die Einrichtung eine einfache konstruktive Vorkehrung darstellt, die in jedem Radialverdichter vorgesehen werden kann, unabhängig seiner technischen Spezifikation. Vorteilhafte und zweckmässige Weiterbildungen der erfindungsgemässen Aufgabenlösung sind in den abhängigen Ansprüchen gekennzeichnet.The main advantage of the invention is that this device behaves neutrally as long as the radial compressor delivers the full volume flow; only when different flow structures occur, in particular at partial load, the device comes into operation and prevents the phenomenon of separation from appearing over the entire partial load range. This prevents the dreaded "pumping", which results in stable characteristics. Another advantage of the invention can be seen in the fact that the device represents a simple structural arrangement that can be provided in any radial compressor, regardless of its technical specification. Advantageous and expedient developments of the task solution according to the invention are characterized in the dependent claims.

Im folgenden wird anhand der Zeichnung Ausführungsbeispiele der Erfindung erläutert. Alle für das unmittelbare Verständnis der Erfindung nicht erforderlichen Elemente sind fortgelassen. Die Strömungsrichtung des Mediums ist mit Pfeilen angegeben.Exemplary embodiments of the invention are explained below with reference to the drawing. All elements not necessary for the immediate understanding of the invention have been omitted. The direction of flow of the medium is indicated by arrows.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Es zeigt:

Fig. 1
einen Radialverdichter mit einer Einrichtung, die die Kennfelderweiterung des Verdichters ermöglicht;
Fig. 2
einen Radialverdichter mit einer konstruktiven Erweiterung der Einrichtung und
Fig. 3
eine massliche Fixierung der Einrichtung.
It shows:
Fig. 1
a radial compressor with a device that enables the map expansion of the compressor;
Fig. 2
a radial compressor with a design extension of the device and
Fig. 3
a massive fixation of the facility.

BESCHREIBUNG DER AUSFÜHRUNGSBEISPIELEDESCRIPTION OF THE EMBODIMENTS

Fig. 1 zeigt eine Teilansicht eines Radialverdichters im Bereich einer vorgesehenen Einrichtung zur Kennfelderweiterung beim Betrieb eines solchen Verdichters. Die Einrichtung bewirkt allgemein eine Stabilisierung der Laufradströmung im Eintrittsbereich bei Teillastbetrieb. Der Radialverdichter besteht aus Gehäuse 1 und Laufrad 2, wobei vor dem Laufrad 2 die obengenannte Stabilisierungseinrichtung vorgesehen ist, welche ihrerseits aus einer Stabilisatoröffnung 5, einem Stabilisierungsring 3 und einer Anzahl Stabilisatorschaufeln 4 besteht. Die Stabilisatoröffnung 5 hat die Form einer Innennut und erstreckt sich in radialer Richtung, ausgehend von der Oberfläche des Eintrittskanals 6, um eine bestimmte Tiefe in das Gehäuse 1 hinein; in axialer Richtung erstreckt sie sich ungefähr ab Zuströmungskante des Laufrades 2 stromaufwärts um eine bestimmte Länge. Der Stabilisierungsring 3 ist in die Stabilisatoröffnung 5 integriert, wobei seine Innenumfangsfläche in die Fortsetzung der Oberfläche des Eintrittskanals 6 verläuft. Der Aussenumfang des Stabilisierungsringes 3 ist mit einer Anzahl Schaufeln bestückt, die in radialer Ausdehnung die verbleibende lichte Weite derStabilisatoröffnung 5 ausfüllen und dort verankert sind. Die Wanddicke des Stabilisierungsringes 3 stellt eine Funktion der betriebsmässig benötigten Festigkeit und Stabilität dar. Aus strömungstechnischen Ueberlegungen darf die Wanddicke des Stabilisierungsringes 3 nicht unnötig auf Kosten der Höhe der Stabilisatorschaufeln 4 gehen. Demnach hat man es hier mit einer beschaufelten Stabilisatorvariante zu tun, welche gegenüber einer unbeschaufelten Ausführung eine bessere Wirkung Richtung Beseitigung eines Hysterese- oder Instabilitätsgebietes garantiert. Zwar bewirkt auch eine unbeschaufelte Ausführung des Stabilisators an sich eine Verkleinerung eines Instabilitätsgebietes, indessen eine Beseitigung desselben lässt sich damit nicht erreichen. Dies hängt weitgehend damit zusammen, dass der auf den vom Verdichter geförderten Volumenstrom bezogene zirkulierende Volumenstrom in den Teillastzuständen bei einem beschaufelten Stabilisator grösser als bei einem unbeschaufelten ist. Diese Unterschiede rühren von den unterschiedlichen Verlustbeiwerten der Stabilisatoren her. Grundsätzlich besteht die richtige Auslegung des Stabilisators vorweg in der richtigen Wahl des Aussendurchmessers des Stabilisierungsringes 3, der jeweils auf den Verdichter, d.h. auf den Aussendurchmesser am Laufradeintritt, so abzustimmen ist, dass einerseits im Bestpunkt nur wenig durch die Stabilisatoröffnung 5 strömt, damit der Wirkungsgrad nicht fällt, andererseits bei Teillast eine möglichst grosse Strömung 8 zirkulieren muss. Natürlich besteht nach festgelegter Wahl des Aussendurchmessers des Stabilisierungsringes 3 eine Interdependenz zwischen diesem und den Abmessungen der anderen Elemente der Einrichtung.Fig. 1 shows a partial view of a radial compressor in the area of an intended device for expanding the map when operating such a compressor. The device generally effects a stabilization of the impeller flow in the inlet area during part-load operation. The radial compressor consists of housing 1 and impeller 2, the above-mentioned stabilization device being provided in front of impeller 2, which in turn consists of a stabilizer opening 5, a stabilization ring 3 and a number of stabilizer blades 4. The stabilizer opening 5 has the shape of an inner groove and extends in the radial direction, starting from the surface of the inlet channel 6, into the housing 1 by a certain depth; in the axial direction it extends approximately upstream by a certain length from the inflow edge of the impeller 2. The stabilization ring 3 is integrated in the stabilizer opening 5, its inner circumferential surface extending into the continuation of the surface of the inlet channel 6. The outer circumference of the stabilizing ring 3 is equipped with a number of blades which, in radial expansion, fill the remaining clear width of the stabilizer opening 5 and are anchored there. The wall thickness of the stabilization ring 3 represents a function of the operationally required strength and stability. For fluidic considerations, the wall thickness of the stabilization ring 3 must not unnecessarily come at the expense of the height of the stabilizer blades 4. Accordingly, one is dealing with a bladed stabilizer variant, which guarantees a better effect towards eliminating a hysteresis or instability area compared to a bladed version. Even if the stabilizer is not bladed in itself, an instability area is reduced in size, but it cannot be eliminated. This is largely due to the fact that the circulating volume flow, based on the volume flow conveyed by the compressor, is greater in the part-load states with a bladed stabilizer than with an unbladed one. These differences result from the different loss coefficients of the stabilizers. Basically, the correct design of the stabilizer consists first of all in the correct choice of the outside diameter of the stabilizing ring 3, which is to be matched to the compressor, that is to say to the outside diameter at the impeller inlet, so that on the one hand only a little flows through the stabilizer opening 5 at the best point, so that the efficiency does not fall, on the other hand, the largest possible flow 8 must circulate at partial load. Of course, after a fixed choice of the outside diameter of the stabilizing ring 3, there is an interdependence between the latter and the dimensions of the other elements of the device.

Hierzu verweisen wir auf die Ausführungen unter Fig. 3. Bei Ueberlast strömt ein Teil des Förderstromes 9 durch die Stabilisatoröffnung 5 in gleicher Strömungsrichtung wie die Hauptströmung 7, beaufschlagt mit letzterer das Laufrad 2, um dann als komprimierte Luft zum Durchgang 10 abzuströmen. In der Stabilisatoröffnung 5 erhält der Teilförderstrom 9 auch einen Gegendrall, wodurch der Wirkungsgrad die Tendenz einnimmt, zu wachsen. Wie aus Fig. 1 des weiteren ersichtlich ist, ist das hier gesagte Ausführungsbeispiel so ausgelegt, dass das Laufrad 2 in die Stabilisatoröffnung 5 hineinragt. Dies hat folgende Bewandtnis: Je weiter das Laufrad 2 in die Stabilisatoröffnung 5 hineinragt, um so mehr Arbeit wird an die zirkulierende Luft übertragen, um so grösser ist der zirkulierende Volumenstrom 8 und um so grösser ist die stabilisierende Wirkung der Einrichtung. Die Breite der Stabilisatorschaufel 4 in Strömungsrichtung der rezirkulierenden Teillast-Strömung 8 ist, wie die gestrichelte Stabilisatorschaufel 4a zeigen will, variabel und kann in dieser Ausdehnungsebene die ganze restliche Breite der Stabilisatoröffnung 5 einnehmen. Eine möglichst breite Stabilisatorschaufel 4a hat kanalisierende Wirkung auf die Teilströme 8, 9 und hilft, die Stabilität der Einrichtung bei Teil- und Ueberlast zu erhöhen.In this regard, we refer to the explanations under FIG. In the stabilizer opening 5, the partial flow 9 also receives a counter-swirl, whereby the efficiency tends to grow. As can also be seen from FIG. 1, the exemplary embodiment mentioned here is designed such that the impeller 2 projects into the stabilizer opening 5. This has the following relevance: The further the impeller 2 protrudes into the stabilizer opening 5, the more work is transferred to the circulating air, the greater the circulating volume flow 8 and the greater the stabilizing effect of the device. The width of the stabilizer blade 4 in the flow direction of the recirculating part-load flow 8 is variable, as the dashed-line stabilizer blade 4a wants to show, and can occupy the entire remaining width of the stabilizer opening 5 in this plane of expansion. The widest possible stabilizer blade 4a has a channeling effect on the partial flows 8, 9 and helps to increase the stability of the device in the event of partial and overload.

Fig. 2 zeigt ebenfalls einen Radialverdichter nach Fig. 1 mit einer Weiterbildung von Stabilisierungsring 3 und Stabilisatorschaufel 4a zum Zwecke, eine Strömungsverbesserung in der Stabilisatoröffnung 5 bei Teillast zu erzielen. Der Stabilisierungsring 3a ist profiliert ausgebildet, während die Stabilisatorschaufel 4a, welche in Strömungsrichtung der Teillastströmung 8 maximale axiale Ausdehnung aufweist, durch eine Einströmungshilfe 4b weitergebildet ist. Diese Massnahmen ermöglichen eine wenn auch kleine Verbesserung der Kennlinien bei Teillast. Fig. 2 zeigt des weiteren ein Beispiel der unter Fig. 1 postulierten Vergrösserung der stabilisierenden Wirkung der Einrichtung durch Erstreckung des Laufrades 2a in Gegenstromrichtung bis weit in die Stabilisatoröffnung 5 hinein. Wie die Figur 2 erkennen lässt, ist es konstruktiv ohne weiteres machbar, das Laufrad 2a bis zum Stabilisierungsring 3a in die Stabilisatoröffnung 5 hineinragen zu lassen.FIG. 2 also shows a radial compressor according to FIG. 1 with a development of the stabilization ring 3 and stabilizer blade 4a for the purpose of achieving a flow improvement in the stabilizer opening 5 under partial load. The stabilization ring 3a is profiled, while the stabilizer blade 4a, which has maximum axial expansion in the flow direction of the partial load flow 8, is further developed by an inflow aid 4b. These measures enable the characteristics to be improved, albeit slightly, at part load. FIG. 2 further shows an example of the increase in the stabilizing effect of the device postulated under FIG. 1 by extending the impeller 2a in the countercurrent direction to far into the stabilizer opening 5. As can be seen in FIG. 2, it is structurally feasible to have the impeller 2a protrude into the stabilizer opening 5 as far as the stabilizing ring 3a.

Für die nachfolgenden Ausführungen wird Fig. 3 zugrundegelegt. Wie in der Beschreibung unter Fig. 1 ausgeführt wurde, besteht die richtige Auslegung des Stabilisators vorweg in der richtigen Wahl des Aussendurchmessers d des Stabilisierungsringes 3. Es ist offensichtlich, dass dieser Durchmesser d in einem bestimmten Verhältnis zum Aussendurchmesser der Laufradeintrittsöffnung Y stehen muss, will man die anvisierten Vorteile aus dem Betrieb eines Radialverdichters mit einer Einrichtung zur Stabilisierung der Laufradströmung im Eintrittsbereich, insbesondere bei Teillast sicherstellen. Eine richtige Wahl des Aussendurchmessers des Stabilisierungsringes d besteht darin, diesen im Intervall 1,02 - 1,05 zum Aussendurchmesser der Laufradeintrittsöffnung Y zu begrenzen. Die Grössen der anderen Elemente der Einrichtung leiten sich von dieser Ausgangswahl ab, wobei nachfolgend die Dimensionen dieser Elemente der Uebersichtlichkeit wegen als Verhältniszahl zum jeweiligen Aussendurchmesser der Laufradeintrittsöffnung Y ausgedrückt werden.3 is used as a basis for the following explanations. As was explained in the description under FIG. 1, the correct design of the stabilizer consists first of all in the correct choice of the outer diameter d of the stabilizing ring 3. It is obvious that this diameter d must be in a certain ratio to the outer diameter of the impeller inlet opening Y. to ensure the envisaged advantages of operating a radial compressor with a device for stabilizing the impeller flow in the inlet area, in particular under partial load. A correct choice of the outer diameter of the stabilizing ring d is to limit it in the interval 1.02 - 1.05 to the outer diameter of the impeller inlet opening Y. The sizes of the other elements of the device are derived from this choice of output, the dimensions of these elements being subsequently expressed for the sake of clarity as a ratio to the respective outer diameter of the impeller inlet opening Y.

Zusammengefasst ergeben sich folgende Relationen:

  • Das Ueberlappungsmass S2 des Laufrades 2 gegenüber der Stabilisatoröffnung 5 steht im Verhältnis 0 - 0,06 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Die Restöffnung S3 zwischen Anfangskante der Stabilisatoröffnung 5 und Anfangskante des Stabilisierungsringes 3 in Strömungsrichtung zum Laufrad 2 steht im Verhältnis 0,06 - 0,12 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Die Breite B1 der Stabilisatorschaufel 4a, gerechnet von der Eintrittskante der Stabilisatoröffnung (5) in Strömungsrichtung, steht im Verhältnis 0,08 - 0,22 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Der Aussendurchmesser D der Stabilisatoröffnung 5 steht im Verhältnis 1,08 - 1,21 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Die aktive Breite B2 der Stabilisatoröffnung 5, die aus der Gesamtbreite der Stabilisatoröffnung 5 abzüglich Ueberlappungsmass S2 resultiert, steht im Verhältnis 0,12 - 0,26 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Die effektive Breite B3 des Stabilisierungsringes 3 steht im Verhältnis 0,06 - 0,16 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Die Spaltöffnung S1 zwischen Endkante des Stabilisierungsringes 3 und Eintrittskante des Laufrades 2 steht im Verhältnis 0 - 0,04 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
  • Der Aussendurchmesser d des Stabilisierungsringes 3 schliesslich steht - wie bereits ausgeführt - im Verhältnis 1,02 - 1,05 zum Aussendurchmesser der Laufradeintrittsöffnung Y.
In summary, the following relations result:
  • The overlap dimension S2 of the impeller 2 with respect to the stabilizer opening 5 is in a ratio of 0-0.06 to the outer diameter of the impeller inlet opening Y.
  • The remaining opening S3 between the start edge of the stabilizer opening 5 and the start edge of the stabilization ring 3 in the flow direction to the impeller 2 is in a ratio of 0.06-0.12 to the outside diameter of the impeller inlet opening Y.
  • The width B1 of the stabilizer blade 4a, calculated from the leading edge of the stabilizer opening (5) in the flow direction, is in a ratio of 0.08-0.22 to the outer diameter of the impeller inlet opening Y.
  • The outer diameter D of the stabilizer opening 5 is in a ratio of 1.08-1.21 to the outer diameter of the impeller inlet opening Y.
  • The active width B2 of the stabilizer opening 5, which results from the total width of the stabilizer opening 5 minus the overlap dimension S2, is in a ratio of 0.12-0.26 to the outer diameter of the impeller inlet opening Y.
  • The effective width B3 of the stabilizing ring 3 is in a ratio of 0.06-0.16 to the outer diameter of the impeller inlet opening Y.
  • The gap opening S1 between the end edge of the stabilizing ring 3 and the leading edge of the impeller 2 is in a ratio of 0-0.04 to the outer diameter of the impeller inlet opening Y.
  • Finally, the outer diameter d of the stabilizing ring 3 is, as already stated, in a ratio of 1.02 to 1.05 to the outer diameter of the impeller inlet opening Y.

Die äusserst engen Intervalle dieser Verhältnisse zeigen deutlich auf, dass die Auslegung einer neuen, optimierten Einrichtung zur Kennfelderweiterung bei Teillasten in einem Radialverdichter ohne vorgängige Laborversuche fixiert werden kann.The extremely narrow intervals of these conditions clearly show that the design of a new, optimized device for expanding the map at partial loads can be fixed in a radial compressor without prior laboratory tests.

Claims (6)

  1. Device for extending the performance of a radial compressor at small throughputs in the inlet region of the impeller of the compressor, characterised in that the device comprises a recess (5) the length (B₂ + S₂) of which is in the ratio of 0.12 - 0.32 to the outside diameter of the inlet aperture (Y) of the impeller (2), in that the recess (5) runs in the circumferential direction of the inlet duct (6) of the radial compressor and which [sic] extends upstream of the inlet aperture (Y) of the impeller (2), which overlaps the edge of the recess (5) furthest away in the flow direction by an overlap dimension (S₂) in the ratio of 0 - 0.06 to the outside diameter of the inlet aperture (Y) of the impeller (2), in that integrated in the recess is a stabilisation ring (3), the outside diameter (d) of which is in the ratio of 1.02 - 1.05 to the outside diameter of the inlet aperture (Y) of the impeller (2), in that the stabilisation ring (3) is arranged ahead of the impeller (2) and outside the principal flow (7) of the delivery medium, and in that the stabilisation ring (3) bears on the outer circumference a number of blades (4, 4a), which for their part are anchored on the inner contour of the recess (5).
  2. Device according to Claim 1, characterised in that between the end edge of the stabilisation ring (3) in the flow direction and the inlet edge of the impeller (2) there is a gap aperture (S₁), the demension of which is in the ratio of 0 - 0.04 to the outside diameter of the inlet aperture (Y) of the impeller (2).
  3. Device according to Claims 1 and 2, characterised in that the width (B₃) of the stabilisation ring (3) is in the ratio of 0.06 - 0.16 to the outside diameter of the inlet aperture (Y) of the impeller (2).
  4. Device according to Claims 1 to 3, characterised in that the aperture (B₂) of the recess (5) which extends from the inlet edge of the latter in the flow direction to the impeller (3) [sic] is in the ratio of 0.12 - 0.26 to the outside diameter of the inlet aperture (Y) of the impeller (2).
  5. Device according to Claims 1 to 4, characterised in that the width (B₁) of the blade (4,4a), calculated from the inlet edge of the recess (5) in the flow direction, is in the ratio of 0.08 - 0.22 to the outside diameter of the inlet aperture (Y) of the impeller (2).
  6. Device according to Claims 1 to 5, characterised in that the outside diameter (D) of the recess (5) is in the ratio of 1.08 - 1.21 to the outside diameter of the inlet aperture (Y) of the impeller (2).
EP89109560A 1988-06-29 1989-05-26 Device for extending the surge margin of a radial compressor Expired - Lifetime EP0348674B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH2478/88A CH675279A5 (en) 1988-06-29 1988-06-29
CH2478/88 1988-06-29
IN485MA1989 IN172509B (en) 1988-06-29 1989-06-20

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EP0348674A1 EP0348674A1 (en) 1990-01-03
EP0348674B1 true EP0348674B1 (en) 1992-12-16

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EP (1) EP0348674B1 (en)
CH (1) CH675279A5 (en)
IN (1) IN172509B (en)
RU (1) RU1831590C (en)

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Also Published As

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RU1831590C (en) 1993-07-30
US4990053A (en) 1991-02-05
JPH0242199A (en) 1990-02-13
CH675279A5 (en) 1990-09-14
IN172509B (en) 1993-09-04
EP0348674A1 (en) 1990-01-03

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