WO2015189234A1 - Compressor for high suction capacity - Google Patents

Compressor for high suction capacity Download PDF

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Publication number
WO2015189234A1
WO2015189234A1 PCT/EP2015/062877 EP2015062877W WO2015189234A1 WO 2015189234 A1 WO2015189234 A1 WO 2015189234A1 EP 2015062877 W EP2015062877 W EP 2015062877W WO 2015189234 A1 WO2015189234 A1 WO 2015189234A1
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WO
WIPO (PCT)
Prior art keywords
blade
sectional area
blades
narrowest cross
compressor
Prior art date
Application number
PCT/EP2015/062877
Other languages
German (de)
French (fr)
Inventor
Daniel Buchwald
Patrick BUCHWALD
Original Assignee
Abb Turbo Systems Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Abb Turbo Systems Ag filed Critical Abb Turbo Systems Ag
Publication of WO2015189234A1 publication Critical patent/WO2015189234A1/en

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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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade

Definitions

  • the invention relates to the field of exhaust gas turbochargers for charging internal combustion engines. It relates to a compressor of a centrifugal compressor and an exhaust gas turbocharger with a compressor with such a compressor wheel.
  • single-stage centrifugal compressors are generally used to increase the intake pressure of the internal combustion engine.
  • the most widely used compressor wheels include a certain number of main blades and one idler blade per main blade.
  • a technology that both reduces product price and increases efficiency provides opportunities to dramatically increase the competitiveness of products across market segments.
  • No. 5,730,582 discloses a compressor wheel whose blades are shaped in such a way that the finished cast compressor wheel can be released from it without destruction of the casting mold.
  • the blades have a specially curved shape for this purpose.
  • the object of the present invention is to provide a compressor with an increased specific absorption capacity.
  • this is achieved by specifically increasing the narrowest cross-sectional area of the flow channels between the blades in the compressor wheel by means of a suitable blade shaping.
  • the blade leading edge of each main blade is configured sickle-shaped in the direction of the blade height, in that the blade is designed curved in the opposite direction to the direction of rotation. This enlarges the narrowest throat area between two adjacent blades.
  • the narrowest cross-sectional area is optionally further increased by bending the blade in the direction of rotation in the region of the throat line, where the narrowest cross-sectional area meets the suction side of the blade.
  • FIG. 1 shows an exhaust gas turbocharger with a radial compressor according to the prior art
  • FIG. 2 shows a compressor wheel of a radial compressor according to FIG. 1
  • FIG. 1 shows an exhaust gas turbocharger with a radial compressor according to the prior art
  • FIG. 2 shows a compressor wheel of a radial compressor according to FIG. 1
  • FIG. 1 shows an exhaust gas turbocharger with a radial compressor according to the prior art
  • FIG. 2 shows a compressor wheel of a radial compressor according to FIG. 1
  • FIG. 3 shows a schematic representation of two adjacently arranged blades of a compressor wheel according to FIG. 2, FIG.
  • FIG. 4 shows a schematic representation of two adjacently arranged blades according to a first exemplary embodiment of a compressor wheel designed according to the invention
  • FIG. 4 shows a schematic illustration of two adjacently arranged blades according to a second exemplary embodiment of a compressor wheel designed according to the invention.
  • FIG. 1 shows a section along the shaft axis through an exhaust gas turbocharger according to the prior art with a radial compressor and an axial turbine.
  • the compressor wheel 1 of the centrifugal compressor is arranged in a compressor housing 2 which limits the flow channels of the air required for combustion in the internal combustion engine.
  • the compressor wheel shown enlarged in FIG. 2 has a hub 10 and a multiplicity of moving blades.
  • the blades are subdivided into main blades 1 1 and 12, which have the full length, and intermediate vanes 15 arranged therebetween, which have an inlet edge which is offset in the direction of flow and thus a reduced length.
  • the term blades is used to refer to the main blades of the compressor wheel.
  • the compressor wheel is mounted on a shaft 4, which is mounted in a bearing housing 3 in the radial and axial directions.
  • the shaft and the compressor wheel attached to it are driven by the turbine wheel 6, which is arranged in a two-part turbine housing.
  • the hot exhaust gases from the combustion chambers of the internal combustion engine are passed through a gas inlet housing 8 on the turbine.
  • a guide device 7 Upstream of the rotor blades of the turbine wheel 6 is a guide device 7, which directs the flow onto the rotor blades.
  • the exhaust gases are supplied through the gas outlet housing 5 to the chimney or exhaust.
  • Each blade 12 of the compressor wheel 1 shown enlarged in Fig. 2 and shown schematically and in part in Fig. 3 has an inlet edge FE.
  • the surface on the pressure side (front of the blade in the direction of rotation) of each blade defines a flow channel.
  • This flow channel has a narrowest cross-sectional area 20, which usually intersects the pressure side of the blade 12 at the leading edge FE or at a certain distance from the leading edge FE.
  • the suction side of the next, adjacent blade cuts the narrowest cross-sectional area due to the oblique arrangement of the blades, however, with a greater distance from the leading edge, as shown in FIG. 2 can be seen.
  • the narrowest cross-sectional area 20 is referred to in the jargon as "Throat Area”, while the cut line TL on the suction side of the blade is commonly referred to as "Throat Line”.
  • the region of the leading edge of each blade is formed with a curvature in order to enlarge the throat area, ie the narrowest cross-sectional area 20 in the flow channel between the blades 11 and 12 of the compressor wheel.
  • the curvature goes against the direction indicated by the arrow running direction of the compressor wheel, so that the blade 12 is formed in the region of the leading edge FE to the pressure side and concave over the blade height. This results in an enlargement of the narrowest cross-sectional area 20 around the edge region designated 20 ' .
  • the concave curvature of the blade is then reduced in the direction of flow, ie from the leading edge in the direction of the trailing edge.
  • the blade changes into a flat shape, as shown in FIG. 4 by means of the auxiliary lines over the blade height.
  • the convex shape changes to the flat shape up to the throat line TL, so that the narrowest cross-sectional area is not reduced by the shape of the blade.
  • the second embodiment according to FIG. 5 goes even further.
  • the blade 12 is concave in the region of the inlet edge EL towards the pressure side and viewed over the blade height, so that the narrowest cross-sectional area in the area of the pressure side around the edge region 20 ' increases .
  • the blade does not just go into one flat shape, but undergoes a bend in the direction of rotation of the compressor wheel in the region of the throat line.
  • a concave shape results in the suction side over the blade height.
  • the narrowest cross-sectional area thus additionally increases in the edge region 20 " on the suction side.

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

Abstract

The inventive compressor for high specific suction capacity has a compressor wheel (1) with rotor blades (11, 12). In the region of the smallest distance (TL) between two adjacent rotor blades (11, 12), the respective rotor blades (11, 12) are formed so as to increase the area (20', 20'') bounded by the two rotor blades (11, 12) in the region of the narrowest point. In that context, the blade leading edge (FE) is configured in a sickle shape (20'), that is to say the leading edge (FE) is curved counter to the direction of rotation of the blades (11, 12). The curvature is reduced in the flow direction, as far as the region of the smallest distance (TL) between two adjacent rotor blades (11, 12), at least to a flat shape, and is preferably even curved in the direction of rotation (20'').

Description

Verd i chter f ü r hohes Sch l uckve rmögen  Beneficiaries for high assets
B E S C H R E I B U N G Technisches Gebiet B E S C H R E I N T S Technical Area
Die Erfindung bezieht sich auf das Gebiet der Abgasturbolader zum Aufladen von Brennkraftmaschinen. Sie betrifft ein Verdichterrad eines Radialverdichters sowie einen Abgasturbolader mit einem Verdichter mit einem derartigen Verdichterrad.  The invention relates to the field of exhaust gas turbochargers for charging internal combustion engines. It relates to a compressor of a centrifugal compressor and an exhaust gas turbocharger with a compressor with such a compressor wheel.
Stand der Technik State of the art
In modernen Abgasturboladern werden zur Erhöhung des Ansaugdrucks der Brennkraftmaschine in der Regel einstufige Radialverdichter eingesetzt. Die meistverbreiteten Verdichterräder umfassen eine bestimmte Anzahl Hauptlaufschaufeln und jeweils eine Zwischenlaufschaufel pro Hauptlaufschaufel.  In modern exhaust gas turbochargers, single-stage centrifugal compressors are generally used to increase the intake pressure of the internal combustion engine. The most widely used compressor wheels include a certain number of main blades and one idler blade per main blade.
Für die Entwicklung konkurrenzfähiger Radialverdichter sind das spezifische Schluckvermögen und der Stufenwirkungsgrad wichtige Grössen. Bessere Wirkungsgrade und damit verbundene Kraftstoffeinsparungen sind insbesondere in Marktsegmenten wichtig, welche sensibel auf den Energieverbrauch reagieren, beispielsweise bei stationären Kraftwerksanwendungen. In Marktsegmenten mit primärem Fokus auf tiefen Anschaffungskosten, beispielsweise Notstromaggregate, ist dagegen ein möglichst geringer Produktpreis vorteilhaft.  For the development of competitive centrifugal compressors the specific absorption capacity and the step efficiency are important quantities. Better efficiencies and associated fuel savings are particularly important in market segments that are sensitive to energy consumption, such as in stationary power plant applications. In market segments with a primary focus on low acquisition costs, such as emergency generators, on the other hand, the lowest possible product price is advantageous.
Eine Technologie, die sowohl den Produktpreis reduziert als auch den Wirkungsgrad erhöht, bietet Möglichkeiten, die Konkurrenzfähigkeit von Produkten über Marktsegmente hinweg drastisch zu steigern.  A technology that both reduces product price and increases efficiency provides opportunities to dramatically increase the competitiveness of products across market segments.
Um die Produktkosten von Radialverdichtern zu reduzieren, wird grundsätzlich versucht, bei gleichem Raddurchmesser das absolute Schluckvermögen zu erhöhen (Erhöhung des spezifischen Radschluckvermögens). Dadurch können die rotierenden Komponenten bei gegebenem Massenstrom kleiner und somit kostengünstiger dimensioniert werden.  In order to reduce the product costs of centrifugal compressors, an attempt is generally made to increase the absolute absorption capacity for the same wheel diameter (increase in the specific wheel-lift capacity). As a result, the rotating components can be dimensioned smaller and thus more cost-effective for a given mass flow.
Bei konventionellen Methoden zur Erhöhung des Schluckvermögens werden die Verdichterschaufeln in radialer Richtung verlängert, um dadurch die Eintrittsfläche zu vergrössern. Dabei nimmt jedoch die Umfangsgeschwindigkeit der Schaufelspitze im Radeintritt - und somit auch die relative Anströmmachzahl - zu, was durch Reibungsverluste, Stossverluste oder Stoss/Grenzschichtinteraktion zu einer Reduktion des Wirkungsgrads führen kann. Conventional methods of increasing the capacity of the compressor extend the compressor blades in the radial direction, thereby increasing the area of entry. However, the peripheral speed of the blade tip in Radeintritt - and thus also the relative Ansträglichachzahl -, which can lead to a reduction of the efficiency by friction losses, shock losses or shock / boundary layer interaction.
DE 10 2012 004 388 A1 offenbart ein Verdichterrad mit Schaufeln mit in Umfangsrichtung bogenförmig ausgebildeten Anströmkanten zur Verbesserung des Geräuschverhaltens. DE 10 2012 004 388 A1 discloses a compressor wheel with blades having circumferentially arcuately formed leading edges for improving the noise behavior.
US 5,730,582 offenbart ein Verdichterrad, dessen Schaufeln derart geformt sind, dass sich das fertig gegossene Verdichterrad ohne Zerstörung der Gussform aus dieser herauslösen lässt. Die Schaufeln weisen hierfür eine speziell gekrümmte Form auf. No. 5,730,582 discloses a compressor wheel whose blades are shaped in such a way that the finished cast compressor wheel can be released from it without destruction of the casting mold. The blades have a specially curved shape for this purpose.
Kurze Darstellung der Erfindung Brief description of the invention
Die Aufgabe der vorliegenden Erfindung besteht darin, einen Verdichter mit einem erhöhten spezifischen Schluckvermögen zu schaffen. The object of the present invention is to provide a compressor with an increased specific absorption capacity.
Erfindungsgemäss wird dies dadurch erreicht, dass die engste Querschnittsfläche der Strömungskanäle zwischen den Schaufeln im Verdichterrad durch eine geeignete Schaufelformgebung gezielt vergrössert wird. Dabei wird die Schaufelvorderkante jeder Hauptschaufel in Richtung der Schaufelhöhe sichelförmig ausgestaltet, indem die Schaufel entgegen der Drehrichtung gewölbt ausgestaltet wird. Dadurch wird die engste Querschnittsfläche (Throat area) zwischen jeweils zwei benachbarten Schaufeln vergrössert.  According to the invention, this is achieved by specifically increasing the narrowest cross-sectional area of the flow channels between the blades in the compressor wheel by means of a suitable blade shaping. In this case, the blade leading edge of each main blade is configured sickle-shaped in the direction of the blade height, in that the blade is designed curved in the opposite direction to the direction of rotation. This enlarges the narrowest throat area between two adjacent blades.
Die engste Querschnittsfläche wird optional noch weiter vergrössert, indem die Schaufel im Bereich der Throat Line, wo die engste Querschnittsfläche auf die Saugseite der Schaufel trifft, in Drehrichtung durchgebogen wird.  The narrowest cross-sectional area is optionally further increased by bending the blade in the direction of rotation in the region of the throat line, where the narrowest cross-sectional area meets the suction side of the blade.
Dabei ist es denkbar, die wirkungsgradsensitiven Schaufelspitzenschnitte wie mit konventionellen Winkelverteilungen zu versehen und lediglich die Schnitte zwischen dem Nabenverlauf und der Schaufelspitze entsprechend auszugestalten. Dadurch wird der Massenstrom durch das Rad erhöht und die maximale Relativmachzahl im Schaufelspitzenschnitt beibehalten resp. kontrolliert.  It is conceivable to provide the efficiency-sensitive blade tip sections as with conventional angular distributions and to configure only the sections between the hub profile and the blade tip accordingly. As a result, the mass flow is increased by the wheel and the maximum Relativmachzahl maintained in the blade tip section resp. controlled.
Weitere Vorteile ergeben sich aus den abhängigen Ansprüchen.  Further advantages emerge from the dependent claims.
Kurze Beschreibung der Zeichnungen Brief description of the drawings
Folgend sind anhand der Figuren beispielhafte Ausführungsformen des erfindungsgemässen Verdichterrades beschrieben. Dabei zeigt Fig.1 einen Abgasturbolader mit einem Radialverdichter nach dem Stand der Technik, Fig. 2 ein Verdichterrad eines Radialverdichters nach Fig. 1 , Exemplary embodiments of the compressor wheel according to the invention are described below with reference to the figures. It shows 1 shows an exhaust gas turbocharger with a radial compressor according to the prior art, FIG. 2 shows a compressor wheel of a radial compressor according to FIG. 1, FIG.
Fig. 3 eine schematische Darstellung zweier benachbart angeordneter Schaufeln eines Verdichterrades nach Fig. 2,  3 shows a schematic representation of two adjacently arranged blades of a compressor wheel according to FIG. 2, FIG.
Fig. 4 eine schematische Darstellung zweier benachbart angeordneter Schaufeln gemäss einer ersten beispielhaften Ausführungsform eines erfindungsgemäss ausgebildeten Verdichterrades, und 4 shows a schematic representation of two adjacently arranged blades according to a first exemplary embodiment of a compressor wheel designed according to the invention, and FIG
Fig. 4 eine schematische Darstellung zweier benachbart angeordneter Schaufeln gemäss einer zweiten beispielhaften Ausführungsform eines erfindungsgemäss ausgebildeten Verdichterrades.  4 shows a schematic illustration of two adjacently arranged blades according to a second exemplary embodiment of a compressor wheel designed according to the invention.
Weg zur Ausführung der Erfindung Way to carry out the invention
Fig. 1 zeigt einen entlang der Wellenachse geführten Schnitt durch einen Abgasturbolader gemäss dem Stand der Technik mit einem Radialverdichter und einer Axialturbine. Das Verdichterrad 1 des Radialverdichters ist in einem Verdichtergehäuse 2 angeordnet, welches die Strömungskanäle der für die Verbrennung in der Brennkraftmaschine benötigten Luft begrenzt. Das in Fig. 2 vergrössert dargestellte Verdichterrad weist eine Nabe 1 0 und eine Vielzahl von Laufschaufeln auf. Die Laufschaufeln sind unterteilt in Hauptschaufeln 1 1 und 12, welche die volle Länge aufweisen, und dazwischen angeordnete Zwischenschaufeln 15, welche über in Strömungsrichtung versetzte Eintrittskante und somit eine reduzierte Länge aufweisen. Im Weiteren wird mit dem Begriff Schaufeln auf die Hauptschaufeln des Verdichterrades Bezug genommen. Das Verdichterrad ist auf einer Welle 4 befestigt, welche in einem Lagergehäuse 3 in radialer und axialer Richtung gelagert ist. Angetrieben wird die Welle und das daran befestigte Verdichterrad durch das Turbinenrad 6, welches in einem zweiteiligen Turbinengehäuse angeordnet ist. Die heissen Abgase aus den Brennkammern der Brennkraftmaschine werden durch ein Gaseintrittsgehäuse 8 auf die Turbine geleitet. Den Laufschaufeln des Turbinenrades 6 vorgeschaltet ist eine Leitvorrichtung 7, welche die Strömung auf die Laufschaufeln ausrichtet. Nach der Turbinenstufe werden die Abgase durch das Gasaustrittsgehäuse 5 dem Kamin oder Auspuff zugeführt. Jede Schaufel 12 des in Fig. 2 vergrössert und in Fig. 3 schematisch und auszugsweise dargestellten Verdichterrades 1 weist eine Eintrittskante FE auf. Zusammen mit der Oberfläche auf der Saugseite (Rückseite der Schaufel in Rotationsrichtung des Verdichterrades) der nächsten, benachbarten Schaufel 1 1 begrenzt die Oberfläche auf der Druckseite (Vorderseite der Schaufel in Rotationsrichtung) jeder Schaufel einen Strömungskanal. Dieser Strömungskanal weist eine engste Querschnittsfläche 20 auf, welche in der Regel die Druckseite der Schaufel 12 an der Eintrittskante FE oder mit einem gewissen Abstand von der Eintrittskante FE schneidet. Die Saugseite der nächsten, benachbarten Schaufel schneidet die engste Querschnittsfläche aufgrund der schrägen Anordnung der Schaufeln hingegen mit einem grösseren Abstand von der Eintrittskante, wie aus der Fig. 2 ersichtlich ist. Die engste Querschnittsfläche 20 wird im Fachjargon als„Throat Area" bezeichnet, während die Schnittlinie TL auf der Saugseite der Schaufel wird geläufig als„Throat Line" bezeichnet wird. 1 shows a section along the shaft axis through an exhaust gas turbocharger according to the prior art with a radial compressor and an axial turbine. The compressor wheel 1 of the centrifugal compressor is arranged in a compressor housing 2 which limits the flow channels of the air required for combustion in the internal combustion engine. The compressor wheel shown enlarged in FIG. 2 has a hub 10 and a multiplicity of moving blades. The blades are subdivided into main blades 1 1 and 12, which have the full length, and intermediate vanes 15 arranged therebetween, which have an inlet edge which is offset in the direction of flow and thus a reduced length. In the following, the term blades is used to refer to the main blades of the compressor wheel. The compressor wheel is mounted on a shaft 4, which is mounted in a bearing housing 3 in the radial and axial directions. The shaft and the compressor wheel attached to it are driven by the turbine wheel 6, which is arranged in a two-part turbine housing. The hot exhaust gases from the combustion chambers of the internal combustion engine are passed through a gas inlet housing 8 on the turbine. Upstream of the rotor blades of the turbine wheel 6 is a guide device 7, which directs the flow onto the rotor blades. After the turbine stage, the exhaust gases are supplied through the gas outlet housing 5 to the chimney or exhaust. Each blade 12 of the compressor wheel 1 shown enlarged in Fig. 2 and shown schematically and in part in Fig. 3 has an inlet edge FE. Along with the surface on the suction side (back of the blade in the direction of rotation of the compressor wheel) of the next adjacent blade 11, the surface on the pressure side (front of the blade in the direction of rotation) of each blade defines a flow channel. This flow channel has a narrowest cross-sectional area 20, which usually intersects the pressure side of the blade 12 at the leading edge FE or at a certain distance from the leading edge FE. The suction side of the next, adjacent blade cuts the narrowest cross-sectional area due to the oblique arrangement of the blades, however, with a greater distance from the leading edge, as shown in FIG. 2 can be seen. The narrowest cross-sectional area 20 is referred to in the jargon as "Throat Area", while the cut line TL on the suction side of the blade is commonly referred to as "Throat Line".
Erfindungsgemäss wird nach Fig. 4 zur Vergrösserung der Throat Area, also der engsten Querschnittsfläche 20 im Strömungskanal zwischen den Schaufeln 1 1 und 12 des Verdichterrades der Bereich der Eintrittskante jeder Schaufel mit einer Wölbung ausgebildet. Die Wölbung geht entgegen der mit dem Pfeil angedeuteten Laufrichtung des Verdichterrades, so dass die Schaufel 12 im Bereich der Eintrittskante FE zur Druckseite hin und über die Schaufelhöhe betrachtet konkav ausgebildet ist. Dadurch ergibt sich eine Vergrösserung der engsten Querschnittsfläche 20 um den mit 20' bezeichneten Randbereich. Die konkave Wölbung der Schaufel wird anschliessend in Strömungsrichtung, also von der Eintrittskante her in Richtung der Austrittskante reduziert. In der ersten Ausführungsform geht die Schaufel ausgehend von dem konkav ausgebildeten Bereich der engsten Querschnittsfläche im Bereich der Eintrittskante in eine flache Form über, wie dies in der Fig. 4 anhand der Hilfslinien über die Schaufelhöhe dargestellt ist. Die Saugseite der nächsten Schaufel 1 1 betrachtend, geht die konvexe Form bis zur Throat Line TL in die flache Form über, so dass die engste Querschnittsfläche nicht durch die Form der Schaufel verkleinert wird. According to the invention, according to FIG. 4, the region of the leading edge of each blade is formed with a curvature in order to enlarge the throat area, ie the narrowest cross-sectional area 20 in the flow channel between the blades 11 and 12 of the compressor wheel. The curvature goes against the direction indicated by the arrow running direction of the compressor wheel, so that the blade 12 is formed in the region of the leading edge FE to the pressure side and concave over the blade height. This results in an enlargement of the narrowest cross-sectional area 20 around the edge region designated 20 ' . The concave curvature of the blade is then reduced in the direction of flow, ie from the leading edge in the direction of the trailing edge. In the first embodiment, starting from the concave region of the narrowest cross-sectional area in the region of the leading edge, the blade changes into a flat shape, as shown in FIG. 4 by means of the auxiliary lines over the blade height. Looking at the suction side of the next blade 1 1, the convex shape changes to the flat shape up to the throat line TL, so that the narrowest cross-sectional area is not reduced by the shape of the blade.
Noch einen Schritt weiter geht die zweite Ausführungsform nach Fig. 5. Wiederum ist die Schaufel 12 im Bereich der Eintrittskante EL zur Druckseite hin und über die Schaufelhöhe betrachtet konkav ausgebildet, so dass sich die engste Querschnittsfläche im Bereich der Druckseite um den Randbereich 20' vergrössert. Nun geht die Schaufel ausgehend von dem konkav ausgebildeten Bereich der Eintrittskante nicht bloss in eine flache Form über, sondern erfährt im Bereich der Throat Line eine Biegung in Rotationsrichtung des Verdichterrades. Dadurch ergibt sich in der Saugseite über die Schaufelhöhe gesehen eine konkave Form. Die engste Querschnittsfläche vergrössert sich damit zusätzlich auch im Randbereich 20" auf der Saugseite. The second embodiment according to FIG. 5 goes even further. Again, the blade 12 is concave in the region of the inlet edge EL towards the pressure side and viewed over the blade height, so that the narrowest cross-sectional area in the area of the pressure side around the edge region 20 ' increases , Now, starting from the concave area of the leading edge, the blade does not just go into one flat shape, but undergoes a bend in the direction of rotation of the compressor wheel in the region of the throat line. As a result, a concave shape results in the suction side over the blade height. The narrowest cross-sectional area thus additionally increases in the edge region 20 " on the suction side.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
1 Verdichterrad  1 compressor wheel
2 Verdichtergehäuse  2 compressor housing
3 Lagergehäuse  3 bearing housing
4 Welle des Abgasturboladers  4 shaft of the exhaust gas turbocharger
5 Gasaustrittsgehäuse der Turbine  5 gas outlet housing of the turbine
6 Turbinenrad der Axialturbine  6 turbine wheel of the axial turbine
7 Leitvorrichtung  7 guide device
8 Gaseintrittsgehäuse der Turbine  8 gas inlet housing of the turbine
10 Nabe des Verdichterrades 10 Hub of the compressor wheel
1 1 , 12 Schaufeln des Verdichterrades 1 1, 12 blades of the compressor wheel
15 Zwischenschaufeln des Verdichterrades  15 intermediate blades of the compressor wheel
20, 20', 20" Engste Querschnittsfläche zwischen zwei benachbarten Schaufeln des 20, 20 ' , 20 " Narrow cross-sectional area between two adjacent blades of the
Verdichterrades  compressor wheel
TL Schnittkurve der engsten Querschnittsfläche mit der Saugseite der  TL sectional curve of the narrowest cross-sectional area with the suction side of the
Schaufel (Throatline)  Shovel (Throatline)
FE Schaufelvorderkante (Frontend)  FE vane leading edge (frontend)
H Nabenverlauf der Schaufel  H Hub profile of the bucket
S Aussenkante der Schaufel  S outer edge of the blade

Claims

P AT E N T A N S P R Ü C H E P AT E N T A N S P R O C H E
Verdichterrad eines Radialverdichters, umfassend eine Nabe (1 0) und eine Vielzahl auf der Nabe angeordnete Schaufeln (1 1 , 12), wobei die Schaufeln des Verdichterrades derart ausgebildet sind, dass sich jeweils zwischen zwei benachbarten Schaufeln (1 1 , 12) eine engste Querschnittsfläche erstreckt, welche engste Querschnittsfläche eine Saugseite einer ersten der beiden Schaufeln (1 1 ) in einem grösseren Abstand von der Vorderkante dieser ersten Schaufel schneidet als der Abstand von der Vorderkante der zweiten der beiden Schaufeln (12) in welchem diese engste Querschnittsfläche eine Druckseite dieser zweiten Schaufel (12) schneidet, dadurch gekennzeichnet, dass  Compressor of a centrifugal compressor, comprising a hub (1 0) and a plurality of arranged on the hub blades (1 1, 12), wherein the blades of the compressor wheel are formed such that in each case between two adjacent blades (1 1, 12) a narrowest Cross-sectional area extends, which narrowest cross-sectional area a suction side of a first of the two blades (1 1) intersects at a greater distance from the leading edge of this first blade than the distance from the leading edge of the second of the two blades (12) in which this narrowest cross-sectional area a pressure side of this second blade (12), characterized in that
die Druckseite jeder Schaufeln (12) entlang des Schnittbereichs mit der engsten Querschnittsfläche zur benachbarten Schaufel zur Vergrösserung der engsten Querschnittsfläche über die Schaufelhöhe gesehen konkav geformt ist, so dass die Schaufeln im Schnittbereich der Druckseite mit der engsten Querschnittsfläche zur benachbarten Schaufel über die Schaufelhöhe gesehen eine Wölbung entgegen der Rotationsrichtung aufweisen, wobei diese Wölbung der Schaufeln in Strömungsrichtung bis zum weiter von der Eintrittskante entfernten Schnittbereich der Saugseite mit der engsten Querschnittsfläche zur benachbarten Schaufel auf der Saugseite zumindest auf eine flache Form reduziert wird. the pressure side of each blade (12) is concave shaped as seen along the sectional area with the narrowest cross-sectional area to the adjacent blade to increase the narrowest cross-sectional area over the blade height, so that the blades in the section area of the pressure side with the narrowest cross-sectional area to the adjacent blade over the blade height seen Have curvature opposite to the direction of rotation, wherein this curvature of the blades is reduced in the flow direction to the further away from the leading edge cutting region of the suction side with the narrowest cross-sectional area to the adjacent blade on the suction side at least on a flat shape.
Verdichterrad nach Anspruch 1 , wobei die Saugseite jeder Schaufel (1 1 ) entlang des Schnittbereichs mit der engsten Querschnittsfläche (20) zwischen den beiden Schaufeln zur Vergrösserung der engsten Querschnittsfläche konkav geformt ist, so dass die Schaufeln im Schnittbereich der Druckseite mit der engsten Querschnittsfläche zur benachbarten Schaufel über die Schaufelhöhe gesehen eine Wölbung entgegen der Rotationsrichtung aufweisen und weiter beabstandet von der Schaufelvorderkante im Schnittbereich mit der engsten Querschnittsfläche zur benachbarten Schaufel auf der Saugseite über die Schaufelhöhe gesehen eine Wölbung in Rotationsrichtung aufweisen.  A compressor wheel according to claim 1, wherein the suction side of each blade (11) is concave along the sectional area with the narrowest cross-sectional area (20) between the two blades to increase the narrowest cross-sectional area so that the blades are in the intersection of the pressure side with the narrowest cross-sectional area seen adjacent blade over the blade height have a curvature opposite to the rotational direction and further spaced from the blade leading edge in the cutting area with the narrowest cross-sectional area to the adjacent blade on the suction side over the blade height have a curvature in the rotational direction.
Verdichterrad nach Anspruch 2, wobei die Schaufeln in Strömungsrichtung über die Schaufelhöhe gesehen aus der entgegen der Rotationsrichtung gewölbten Form in eine in Rotationsrichtung gewölbte Form und dann in eine flache Form übergehen. Compressor wheel according to claim 2, wherein the blades in the flow direction over the blade height seen from the counter-rotating curved shape in a rotationally curved shape and then in a flat shape.
4. Abgasturbolader, gekennzeichnet durch einen Radialverdichter mit einem Verdichterrad nach einem der Ansprüche 1 bis 3. 4. Exhaust gas turbocharger, characterized by a centrifugal compressor with a compressor wheel according to one of claims 1 to 3.
PCT/EP2015/062877 2014-06-12 2015-06-10 Compressor for high suction capacity WO2015189234A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014108268.0 2014-06-12
DE102014108268 2014-06-12

Publications (1)

Publication Number Publication Date
WO2015189234A1 true WO2015189234A1 (en) 2015-12-17

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5730582A (en) * 1997-01-15 1998-03-24 Essex Turbine Ltd. Impeller for radial flow devices
EP1788255A1 (en) * 2005-11-16 2007-05-23 Siemens Aktiengesellschaft Impeller of radial compressor
US20120263599A1 (en) * 2011-04-13 2012-10-18 Hitachi Plant Technologies, Ltd. Impeller and turbomachinery including the impeller
WO2012161849A1 (en) * 2011-05-23 2012-11-29 Cameron International Corporation Sculpted impeller
DE102012004388A1 (en) * 2012-03-03 2013-09-05 Daimler Ag Wheel for radial compressor utilized for compressing air in supercharger of turbo-charged petrol engine of commercial vehicle, has leading edge including longitudinal region that comprises angle with impeller edge in specific range

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5730582A (en) * 1997-01-15 1998-03-24 Essex Turbine Ltd. Impeller for radial flow devices
EP1788255A1 (en) * 2005-11-16 2007-05-23 Siemens Aktiengesellschaft Impeller of radial compressor
US20120263599A1 (en) * 2011-04-13 2012-10-18 Hitachi Plant Technologies, Ltd. Impeller and turbomachinery including the impeller
WO2012161849A1 (en) * 2011-05-23 2012-11-29 Cameron International Corporation Sculpted impeller
DE102012004388A1 (en) * 2012-03-03 2013-09-05 Daimler Ag Wheel for radial compressor utilized for compressing air in supercharger of turbo-charged petrol engine of commercial vehicle, has leading edge including longitudinal region that comprises angle with impeller edge in specific range

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