EP3161325A1 - Diffuser for a radial compressor - Google Patents

Diffuser for a radial compressor

Info

Publication number
EP3161325A1
EP3161325A1 EP15730184.7A EP15730184A EP3161325A1 EP 3161325 A1 EP3161325 A1 EP 3161325A1 EP 15730184 A EP15730184 A EP 15730184A EP 3161325 A1 EP3161325 A1 EP 3161325A1
Authority
EP
European Patent Office
Prior art keywords
vanes
diffuser
adjacent
angular
centrifugal compressor
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.)
Withdrawn
Application number
EP15730184.7A
Other languages
German (de)
French (fr)
Inventor
Daniel Rusch
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.)
Accelleron Industries AG
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 EP3161325A1 publication Critical patent/EP3161325A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F05D2260/961—Preventing, counteracting or reducing vibration or noise by mistuning rotor blades or stator vanes with irregular interblade spacing, airfoil shape
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to the field of exhaust gas turbochargers for supercharged internal combustion engines. It relates to a bladed diffuser of a centrifugal compressor such exhaust gas turbocharger and an exhaust gas turbocharger with a centrifugal compressor with such a bladed diffuser in its outflow region.
  • single-stage centrifugal compressors with bladed diffusers are generally used downstream of the compressor wheel to increase the intake pressure of the engine to increase the intake pressure of the engine.
  • the kinetic energy of the medium to be compressed is converted into static pressure.
  • the compressor wheels comprise a certain number of blades and the diffusers have vanes with prismatic, typically aerodynamic profiles (wedge or airfoil shape). Viewed in the direction of the compressor axis, the vanes have a certain tangential angle at the leading edge (entry angle), a certain tangential angle at the exit edge (exit angle), and a certain circumferential angular distance between each two adjacent vanes.
  • EP 2014925 A1 discloses how outflow areas of radial compressors can be optimized by diffusers with irregularly distributed guide vanes. For example, seventeen vanes are arranged distributed in two groups of nine or eight vanes, each on a half ring segment.
  • the narrowest sectional area between two vanes is not constant in the above example with seventeen vanes circumferentially, with the narrowest cross-sectional areas being round due to the smaller spacing between the individual vanes in a nine-vaned cluster 3 to 5 percent smaller than in the group of eight vanes, resulting in a different ratio of the flow passages at the compressor impeller outlet and at the diffuser inlet over the circumference, which could adversely affect the efficiency and the stability of the compressor stage.
  • the object of the present invention is to improve the outflow region of a radial compressor in such a way that the partial flow channels in the bladed diffuser have constant narrowest cross-sectional areas (throat area) distributed over the circumference despite the unequally distributed arrangement of the guide vanes.
  • This is achieved according to the invention in that the vanes of the diffuser distributed over the circumference have partially deviating relative angular positions.
  • deviating, relative angular position is meant that two by rotation about the axis superimposed vanes have a different angular orientation.
  • the inventive design of the diffuser of a centrifugal compressor increases the efficiency of the compressor stage and has a positive effect on the surge margin.
  • FIG. 1 shows a section along the compressor axis through a radial compressor with a bladed diffuser
  • Fig. 2 shows a section perpendicular to the compressor axis through a first
  • Embodiment of an inventively designed diffuser with irregularly arranged vanes Embodiment of an inventively designed diffuser with irregularly arranged vanes
  • Fig. 3 shows a section perpendicular to the compressor axis by a second
  • Diffusers are arranged distributed.
  • Fig. 1 shows the radial compressor of an exhaust gas turbocharger in section through the shaft axis.
  • the compressor comprises a compressor wheel arranged on the shaft 12, which comprises a hub 10 and rotor blades 1 1 arranged thereon.
  • the blades may be subdivided into main and intermediate vanes, the main vanes extending the full length of the flow channel defined by the hub and adjacent housing part, while the intermediate vanes are typically shortened and have a recessed leading edge.
  • one or more intermediate blades per main blade can be arranged.
  • the compressor wheel is arranged in the compressor housing, which generally comprises several parts, such as the volute casing 31 and the inlet housing 32. Between the compressor and the turbine, not shown, there is the bearing housing 30, which includes the bearing of the shaft.
  • the already mentioned flow channel in the region of the compressor is limited by the compressor housing.
  • the diffuser In the area of Ver Whyrrades takes over the hub of the compressor wheel, the radially inner boundary, wherein the blades of the compressor wheel are arranged in the flow channel.
  • the diffuser In the flow direction of the medium to be compressed downstream of the compressor wheel, the diffuser is arranged.
  • the diffuser serves, as mentioned above, the slowing down of the accelerated by the compressor wheel flow. This is done on the one hand by the guide vanes 21 of the diffuser, on the other hand by the volute casing, from where the compressed medium is supplied to the combustion chambers of an internal combustion engine.
  • the vanes of the diffuser are connected to one or both sides of the flow channel with a diffuser wall 22, a housing part. Each two vanes of the diffuser arranged adjacent to one another bound together with the diffuser walls a diffuser channel.
  • the diffuser serving as the basis for the invention described here has a plurality of stator blades with at least partially different angular distances.
  • the angle distance between the entry edges of two adjacently arranged vanes is referred to here as the angular distance.
  • the angle between two other, corresponding points of two adjacently arranged vanes may be referred to as angular distance, then, for example, when the leading edges are at different radii.
  • the angular distance can be referred to as the angle between the exit edges or the angle between the profile centers.
  • the angular distances between adjacently arranged vanes are therefore not identical over the entire circumference.
  • the angular distances a x are different for all pairs of guide vanes 21 of the diffuser arranged adjacent to one another, ie no two of the illustrated angular distances between two adjacent vanes are identical.
  • angular distances ao, CM, C (2, C (3) are also distributed irregularly in the example shown
  • the angular distances could also increase or decrease regularly in a circumferential direction, or only increase and then decrease again be achieved when the angular distances of a harmonic function, such as the sine function, following and greater get smaller.
  • two angular distances ao and ai are distributed over two groups of guide vanes. On the left half of the diffuser, a group with eight vanes 210, on the right half of a group with nine vanes 21 1 is arranged.
  • the guide vanes are oriented such that the narrowest cross-sectional area T extending in each case in the diffuser channel between two adjacently arranged guide vanes over the blade height is constant. This is achieved in that the guide vanes are oriented differently, ie have different angular positions ßo, ßi, ß2, ß3 relative to the Tangentialline at the leading edge. Depending on the relative degree of steepness of two adjacently arranged blades, the position of the narrowest cross-sectional area T migrates along the blade surface.
  • the narrowest cross-sectional area T intersects the corresponding guide blade in each case in the region of the blade inlet edge, while on the suction side the intersection line of the narrowest cross-sectional area with the respective guide blade can sometimes move all the way to the end of the guide blade.
  • the respective relative degree of steepness between two guide vanes of a group is relatively constant due to the constant angular spacing, that is to say the respective relative angular position is approximately constant. Deviating angular positions, however, result in the transitional region of the two groups. Further, not shown embodiments are also possible. In this case, for example, all angular distances of the guide vanes can be identical except for one or a few.
  • the individual vanes of the diffuser may differ in shape, length, entry and exit angles, and entry and exit radii, to introduce additional inequalities into the diffuser.
  • the different training can be done both in the axial direction (with respect to the compressor axis), ie in the direction of the blade height, as well as in the circumferential direction. In this case, all or only a few guide vanes can be shaped or arranged differently.
  • Such irregularly formed diffusers may be formed in one or more stages, with several stages arranged in the radial direction one behind the other, ie concentrically with respect to the compressor axis.
  • the narrowest cross-sectional area in the diffuser channel between two vanes and above the diffuser channel height is constant. If the diffuser has a variable, ie non-constant, diffuser channel height distributed over the circumference, the guide vanes are to be arranged in accordance with the invention so that the narrowest cross-sectional area calculated from the spacing between the adjacent guide vanes and the diffuser channel height is constant.
  • the irregularly formed in the circumferential direction diffuser can be positioned with respect to the circumferentially asymmetric spiral housing in a fixed angular position.
  • the size of the different angular distances and their distribution along the circumference can be aligned with the asymmetrically formed volute casing downstream of the guide vanes.
  • the angular distances can increase, for example, along the circumference analogous to the radius of the spiral housing.
  • Leitschaufelplo which is arranged in the region of the Spiralzept culinarys, may have a different angular distance from the other Leitschaufelbin.
  • positioning means ensure that the diffuser is in each case in the intended angular position relative to the spiral housing.
  • the envisaged angular position is advantageously the one in which a minimum resonance oscillation is generated during operation.
  • This angular position from diffuser to volute with minimal resonant vibration generation can optionally be calculated or determined experimentally.
  • a possible positioning means is indicated in Fig. 2, with a positioning cam 23 on the radially outer edge of the diffuser wall 22, which engages in a positioning groove 33 in the spiral housing.
  • Other positive positioning means are conceivable, such as a positioning pin, which is arranged in recesses bored on both sides.
  • the indirect positioning via a third component, such as the inlet housing 32 or the bearing housing 30 are conceivable. LIST OF REFERENCE NUMBERS

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)

Abstract

According to the invention, the resonant vibration of the compressor can be reduced by varying the angular distances between two adjoining guide vanes (21) of the diffuser along the circumference. Additionally, the throat area between adjoining guide vanes is kept constant, which increases efficiency and positively affects the surge margin.

Description

Diffuser fü r Rad ialverd ichter  Diffuser for radial ialverd ichter
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 für aufgeladene Brennkraftmaschinen. Sie betrifft einen beschaufelten Diffusor eines Radialverdichters solcher Abgasturbolader sowie einen Abgasturbolader mit einem Radialverdichter mit einem derartigen beschaufelten Diffusor in seinem Abströmbereich.  The invention relates to the field of exhaust gas turbochargers for supercharged internal combustion engines. It relates to a bladed diffuser of a centrifugal compressor such exhaust gas turbocharger and an exhaust gas turbocharger with a centrifugal compressor with such a bladed diffuser in its outflow region.
In modernen Abgasturboladern werden zur Erhöhung des Ansaugdrucks des Motors in der Regel einstufige Radialverdichter mit beschaufelten Diffusoren stromabwärts des Verdichterrades eingesetzt. Im Diffusor wird die kinetische Energie des zu verdichtenden Mediums in statischen Druck umgewandelt. Die Verdichterräder umfassen eine bestimmte Anzahl Laufschaufeln und die Diffusoren weisen Leitschaufeln mit prismatischen, in der Regel aerodynamischen Profilen (Keil- oder Tragflächenform) auf. In Richtung der Verdichterachse betrachtet haben die Leitschaufeln einen bestimmten tangentialen Winkel an der Eintrittskante (Eintrittswinkel), einen bestimmten tangentialen Winkel an der Austrittskante (Austrittswinkel) sowie einen bestimmten Winkelabstand in Umfangsrichtung zwischen jeweils zwei benachbart zueinander angeordneten Leitschaufeln. In modern exhaust gas turbochargers, single-stage centrifugal compressors with bladed diffusers are generally used downstream of the compressor wheel to increase the intake pressure of the engine to increase the intake pressure of the engine. In the diffuser, the kinetic energy of the medium to be compressed is converted into static pressure. The compressor wheels comprise a certain number of blades and the diffusers have vanes with prismatic, typically aerodynamic profiles (wedge or airfoil shape). Viewed in the direction of the compressor axis, the vanes have a certain tangential angle at the leading edge (entry angle), a certain tangential angle at the exit edge (exit angle), and a certain circumferential angular distance between each two adjacent vanes.
Bei der Auslegung von Verdichterstufen muss stets ein Kompromiss zwischen der aerodynamischen Performance, der mechanischen Auslastung und der Lärmbildung durch den Verdichter gefunden werden. Moderne Verdichterstufen mit hohen spezifischen Schluckvermögen haben lange, dünne Laufschaufeln, deren Eigenformen bei niedrigen Frequenzen auftreten und sich leicht anregen und in Schwingung versetzen lassen. Eine Hauptquelle dieser Anregungen ist ein durch die Leitschaufeln des Diffusors erzeugtes Druckpotenzialfeld. Durch gezielt unregelmässig angeordnete Diffusorleitschaufeln können Resonanzschwingungen vermieden werden, welche ansonsten in den Verdichterlaufschaufeln zu Langzeitermüdung (high cycle fatigue - HCF) und mechanischen Schäden verursachen könnten. Stand der Technik When designing compressor stages, a compromise must always be found between the aerodynamic performance, the mechanical load and the noise generated by the compressor. Modern compressor stages with high specific absorption capacity have long, thin blades whose characteristic forms occur at low frequencies and are easily stimulated and vibrated. A major source of these suggestions is a pressure potential field generated by the vanes of the diffuser. By selectively irregularly arranged diffuser vanes resonant vibrations can be avoided, which could otherwise cause in the compressor blades to long-cycle fatigue (HCF) and mechanical damage. State of the art
EP 2014925 A1 (US2010/0150709) offenbart, wie Abströmbereiche von Radialverdichter durch Diffusoren mit unregelmässig verteilten Leitschaufeln optimiert werden können. Beispielsweise werden dabei siebzehn Leitschaufeln in zwei Gruppen zu jeweils neun beziehungsweise acht Leitschaufeln auf jeweils einem halben Ringsegment verteilt angeordnet.  EP 2014925 A1 (US2010 / 0150709) discloses how outflow areas of radial compressors can be optimized by diffusers with irregularly distributed guide vanes. For example, seventeen vanes are arranged distributed in two groups of nine or eight vanes, each on a half ring segment.
Bei dieser unregelmässigen Anordnung der Leitschaufeln ergeben sich entlang des Umfangs unterschiedliche Strömungskanalquerschnitte zwischen jeweils zwei benachbarten Leitschaufel paaren. Die im Fachjargon mit „Throat Area" bezeichnete engste Querschnittsflächen zwischen zwei Leitschaufeln sind im oben genannten Beispiel mit siebzehn Schaufeln über den Umfang gesehen nicht konstant. Dabei sind die engsten Querschnittsflächen aufgrund des geringeren Abstandes zwischen den einzelnen Schaufeln in der einen Gruppe mit neun Leitschaufeln rund 3 bis 5 Prozent kleiner als in der Gruppe mit acht Leitschaufeln. Dadurch ergibt sich über den Umfang verteilt ein unterschiedliches Verhältnis der Strömungskanäle am Verdichterradaustritt und am Diffusoreintritt, was den Wirkungsgrad und die Stabilität der Verdichterstufe ungünstig beeinträchtigen könnte. In this irregular arrangement of the vanes arise along the circumference different flow channel cross sections between each two adjacent vane pair. The narrowest sectional area between two vanes, referred to in the jargon as "throat area", is not constant in the above example with seventeen vanes circumferentially, with the narrowest cross-sectional areas being round due to the smaller spacing between the individual vanes in a nine-vaned cluster 3 to 5 percent smaller than in the group of eight vanes, resulting in a different ratio of the flow passages at the compressor impeller outlet and at the diffuser inlet over the circumference, which could adversely affect the efficiency and the stability of the compressor stage.
Abströmbereiche von Radialverdichter mit Diffusoren mit unregelmässig verteilten Leitschaufeln sind weiter in JP2010-151032 und JP1993-026198 offenbart. Kurze Darstellung der Erfindung Outflow areas of centrifugal compressors with diffusers having irregularly distributed vanes are further disclosed in JP2010-151032 and JP1993-026198. Brief description of the invention
Die Aufgabe der vorliegenden Erfindung besteht darin, den Abströmbereich eines Radialverdichters dahingehend zu verbessern, dass die Teilströmungskanäle im beschaufelten Diffusor trotz ungleich verteilter Anordnung der Leitschaufeln über den Umfang verteilt konstante engste Querschnittsflächen (Throat Area) aufweisen. Erfindungsgemäss wird dies erreicht, indem die über den Umfang verteilten Leitschaufeln des Diffusors teilweise voneinander abweichende relative Winkellagen aufweisen. Mit abweichender, relativer Winkellage ist dabei gemeint, dass zwei durch Rotation um die Achse übereinander gelegte Leitschaufeln eine unterschiedliche Winkelausrichtung aufweisen. Die erfindungsgemässe Ausgestaltung des Diffusors eines Radialverdichters erhöht den Wirkungsgrad der Verdichterstufe und hat eine positive Auswirkung auf den Pumpgrenzenabstand. The object of the present invention is to improve the outflow region of a radial compressor in such a way that the partial flow channels in the bladed diffuser have constant narrowest cross-sectional areas (throat area) distributed over the circumference despite the unequally distributed arrangement of the guide vanes. This is achieved according to the invention in that the vanes of the diffuser distributed over the circumference have partially deviating relative angular positions. By deviating, relative angular position is meant that two by rotation about the axis superimposed vanes have a different angular orientation. The inventive design of the diffuser of a centrifugal compressor increases the efficiency of the compressor stage and has a positive effect on the surge margin.
Weitere Vorteile ergeben sich aus den abhängigen Ansprüchen. Kurze Beschreibung der Zeichnungen Further advantages emerge from the dependent claims. Brief description of the drawings
Nachfolgend werden anhand der Figuren Ausführungsformen des erfindungsgemäss ausgebildeten Diffusors eines Radialverdichters beschrieben. Dabei zeigt:  Hereinafter, embodiments of the inventively designed diffuser of a centrifugal compressor will be described with reference to FIGS. Showing:
Fig. 1 einen Schnitt entlang der Verdichterachse durch einen Radialverdichter mit einem beschaufelten Diffusor, Fig. 2 einen Schnitt senkrecht zur Verdichterachse durch eine erste 1 shows a section along the compressor axis through a radial compressor with a bladed diffuser, Fig. 2 shows a section perpendicular to the compressor axis through a first
Ausführungsform eines erfindungsgemäss ausgebildeten Diffusors mit unregelmässig angeordneten Leitschaufeln, und  Embodiment of an inventively designed diffuser with irregularly arranged vanes, and
Fig. 3 einen Schnitt senkrecht zur Verdichterachse durch eine zweite Fig. 3 shows a section perpendicular to the compressor axis by a second
Ausführungsform eines erfindungsgemäss ausgebildeten Diffusors mit zwei ungleich grossen Gruppen von Leitschaufeln welche je über die Hälfte des Embodiment of an inventively designed diffuser with two unequal groups of vanes which each over half of the
Diffusors verteilt angeordnet sind. Diffusers are arranged distributed.
Weg zur Ausführung der Erfindung Way to carry out the invention
Fig. 1 zeigt den Radialverdichter eines Abgasturboladers im Schnitt durch die Wellenachse. Der Verdichter umfasst ein auf der Welle 12 angeordnetes Verdichterrad, welches eine Nabe 10 und darauf angeordneten Laufschaufeln 1 1 umfasst. Die Laufschaufeln können in Haupt- und Zwischenschaufeln unterteilt sein, wobei sich die Hauptschaufeln über die gesamte Länge des von der Nabe und dem angrenzenden Gehäuseteils begrenzten Strömungskanals erstrecken, während die Zwischenschaufeln in der Regel verkürzt ausgebildet sind und eine zurückversetzte Eintrittskante aufweisen. Dabei können eine oder mehrere Zwischenschaufeln pro Hauptschaufel angeordnet sein. Das Verdichterrad ist im Verdichtergehäuse angeordnet, welches in der Regel mehrere Teile umfasst, etwa das Spiralgehäuse 31 und das Eintrittsgehäuse 32. Zwischen dem Verdichter und der nicht dargestellten Turbine befindet sich das Lagergehäuse 30, welches die Lagerung der Welle beinhaltet. Der bereits erwähnte Strömungskanal im Bereich des Verdichters wird durch das Verdichtergehäuse begrenzt. Im Bereich des Verdichterrades übernimmt die Nabe des Verdichterrades die radial innere Begrenzung, wobei die Laufschaufeln des Verdichterrades im Strömungskanal angeordnet sind. In Strömungsrichtung des zu verdichtenden Mediums stromab des Verdichterrades ist der Diffusor angeordnet. Der Diffusor dient, wie eingangs erwähnt, der Verlangsamung der durch das Verdichterrad beschleunigten Strömung. Dies erfolgt einerseits durch die Leitschaufeln 21 des Diffusors, andererseits durch das Spiralgehäuse, von wo aus das verdichtete Medium den Brennkammern einer Brennkraftmaschine zugeführt wird. Die Leitschaufeln des Diffusors sind ein- oder beidseitig des Strömungskanals mit einer Diffusor-Wand 22, einem Gehäuseteil, verbunden. Jeweils zwei benachbart zueinander angeordnete Leitschaufeln des Diffusors begrenzen zusammen mit den Diffusor-Wänden einen Diffusor-Kanal. Fig. 1 shows the radial compressor of an exhaust gas turbocharger in section through the shaft axis. The compressor comprises a compressor wheel arranged on the shaft 12, which comprises a hub 10 and rotor blades 1 1 arranged thereon. The blades may be subdivided into main and intermediate vanes, the main vanes extending the full length of the flow channel defined by the hub and adjacent housing part, while the intermediate vanes are typically shortened and have a recessed leading edge. In this case, one or more intermediate blades per main blade can be arranged. The compressor wheel is arranged in the compressor housing, which generally comprises several parts, such as the volute casing 31 and the inlet housing 32. Between the compressor and the turbine, not shown, there is the bearing housing 30, which includes the bearing of the shaft. The already mentioned flow channel in the region of the compressor is limited by the compressor housing. In the area of Verdichterrades takes over the hub of the compressor wheel, the radially inner boundary, wherein the blades of the compressor wheel are arranged in the flow channel. In the flow direction of the medium to be compressed downstream of the compressor wheel, the diffuser is arranged. The diffuser serves, as mentioned above, the slowing down of the accelerated by the compressor wheel flow. This is done on the one hand by the guide vanes 21 of the diffuser, on the other hand by the volute casing, from where the compressed medium is supplied to the combustion chambers of an internal combustion engine. The vanes of the diffuser are connected to one or both sides of the flow channel with a diffuser wall 22, a housing part. Each two vanes of the diffuser arranged adjacent to one another bound together with the diffuser walls a diffuser channel.
Um wie eingangs beschrieben Langzeitermüdung in den Laufschaufeln des Verdichterrades zu verhindern, weist der als Basis für die hier beschriebene Erfindung dienende Diffusor mehrere Leitschaufeln mit zumindest teilweise unterschiedlichen Winkelabständen auf. Als Winkelabstand wird hier der Winkel zwischen den Eintrittskanten zweier benachbart zueinander angeordneten Leitschaufeln bezeichnet. Optional kann als Winkelabstand auch der Winkel zwischen zwei anderen, sich entsprechenden Punkten zweier benachbart zueinander angeordneter Leitschaufeln bezeichnet werden, dann etwa, wenn die Eintrittskanten sich auf unterschiedlichen Radien befinden. In diesem Fall kann als Winkelabstand etwa der Winkel zwischen den Austrittskanten oder der Winkel zwischen den Profilmittelpunkten bezeichnet werden. Die Winkelabstände zwischen benachbart zueinander angeordneten Leitschaufeln sind also nicht über den gesamten Umfang identisch. Dabei gibt es mehrere Möglichkeiten, Diffusoren mit variierenden Winkelabständen zwischen den Leitschaufeln zu realisieren: In einer ersten Ausführungsform gemäss Fig. 2 sind die Winkelabstände axfür alle Paare von benachbart zueinander angeordneten Leitschaufeln 21 des Diffusors unterschiedlich, das heisst keine zwei der dargestellten Winkelabständen zwischen jeweils zwei benachbarten Leitschaufeln sind identisch. In order to prevent long-term fatigue in the rotor blades of the compressor wheel as described above, the diffuser serving as the basis for the invention described here has a plurality of stator blades with at least partially different angular distances. The angle distance between the entry edges of two adjacently arranged vanes is referred to here as the angular distance. Optionally, the angle between two other, corresponding points of two adjacently arranged vanes may be referred to as angular distance, then, for example, when the leading edges are at different radii. In this case, the angular distance can be referred to as the angle between the exit edges or the angle between the profile centers. The angular distances between adjacently arranged vanes are therefore not identical over the entire circumference. There are several possibilities to realize diffusers with varying angular distances between the guide vanes: In a first embodiment according to FIG. 2, the angular distances a x are different for all pairs of guide vanes 21 of the diffuser arranged adjacent to one another, ie no two of the illustrated angular distances between two adjacent vanes are identical.
Die unterschiedlichen Winkelabstände ao, CM , C(2, C(3 sind im dargestellten Beispiel zudem unregelmässig verteilt. Alternativ könnten die Winkelabstände auch regelmässig in eine Umfangsrichtung zu- bzw. abnehmen, oder erst zu- und dann wieder abnehmen. Besonders vorteilhafte Ergebnisse können erzielt werden, wenn die Winkelabstände einer harmonischen Funktion, beispielsweise der Sinusfunktion, folgend grösser und kleiner werden. In einer zweiten Ausführungsform gemäss Fig. 3 sind zwei Winkelabstände ao und ai auf zwei Gruppen von Leitschaufeln verteilt. Auf der linken Hälfte des Diffusors ist eine Gruppe mit acht Leitschaufeln 210, auf der rechten Hälfte eine Gruppe mit neun Leitschaufeln 21 1 angeordnet. In beiden Ausführungsformen sind die Leitschaufeln derart ausgerichtet, dass die sich jeweils im Diffusor-Kanal zwischen zwei benachbart angeordneten Leitschaufeln über die Schaufelhöhe erstreckende, engste Querschnittsfläche T konstant ist. Dies wird dadurch erreicht, dass die Leitschaufeln unterschiedlich ausgerichtet sind, also relativ zur Tangentiallinie an der Eintrittskante unterschiedliche Winkellagen ßo, ßi, ß2, ß3 aufweisen. Je nach relativem Steilheitsgrad zweier benachbart angeordneter Schaufeln wandert die Lage der engsten Querschnittsfläche T entlang der Schaufeloberfläche. Auf der Druckseite schneidet die engste Querschnittsfläche T dabei die entsprechende Leitschaufel jeweils im Bereich der Schaufeleintrittskante, während auf der Saugseite die Schnittlinie der engsten Querschnittsfläche mit der jeweiligen Leitschaufel mitunter bis ganz ans Ende der Leitschaufel wandern kann. In der Ausführungsform nach Fig. 3 ist der jeweilige relative Steilheitsgrad zwischen zwei Leitschaufeln einer Gruppe aufgrund des konstanten Winkelabstands relativ konstant, die jeweilige relative Winkellage also in etwa gleichbleibend. Abweichende Winkellagen ergeben sich jedoch im Übergangsbereich der beiden Gruppen. Weitere, nicht dargestellte Ausführungsformen sind ebenfalls möglich. Dabei können beispielsweise alle Winkelabstände der Leitschaufeln bis auf einen oder einige wenige identisch sein. Es können mehr als zwei Gruppen mit jeweils identischen Winkelabständen gebildet werden. Diese Paarungen von Leitschaufeln mit identischen Winkelabständen können aneinander gereiht oder voneinander getrennt angeordnet sein. Optional können sich die einzelnen Leitschaufeln des Diffusors in Form, Länge, Eintritts- und Austrittswinkel sowie Eintritts- und Austrittsradius voneinander unterscheiden, um zusätzliche Ungleichheiten in den Diffusor einzubringen. Die unterschiedliche Ausbildung kann dabei sowohl in axialer Richtung (bezüglich der Verdichterachse), also in Richtung der Schaufelhöhe, wie auch in Umfangsrichtung erfolgen. Dabei können alle oder nur einige wenige Leitschaufeln unterschiedlich geformt oder angeordnet sein. Solche unregelmässig ausgebildete Diffusoren können in ein- oder mehrstufiger Form ausgebildet sein, wobei bei mehreren Stufen diese in radialer Richtung hintereinander, also konzentrisch bezüglich der Verdichterachse, angeordnet sind. Erfindungsgemäss ist bei allen diesen Ausführungsformen die engste Querschnittsfläche im Diffusor-Kanal zwischen zwei Leitschaufeln und über der Diffusor-Kanalhöhe konstant. Weist der Diffusor über den Umfang verteilt eine variable, also nicht konstante Diffusor-Kanalhöhe auf, sind die Leitschaufeln erfindungsgemäss so anzuordnen, dass die jeweils aus dem Abstand der benachbarten Leitschaufeln und der Diffusor-Kanalhöhe berechnete engste Querschnittsfläche konstant ist. The different angular distances ao, CM, C (2, C (3) are also distributed irregularly in the example shown Alternatively, the angular distances could also increase or decrease regularly in a circumferential direction, or only increase and then decrease again be achieved when the angular distances of a harmonic function, such as the sine function, following and greater get smaller. In a second embodiment according to FIG. 3, two angular distances ao and ai are distributed over two groups of guide vanes. On the left half of the diffuser, a group with eight vanes 210, on the right half of a group with nine vanes 21 1 is arranged. In both embodiments, the guide vanes are oriented such that the narrowest cross-sectional area T extending in each case in the diffuser channel between two adjacently arranged guide vanes over the blade height is constant. This is achieved in that the guide vanes are oriented differently, ie have different angular positions ßo, ßi, ß2, ß3 relative to the Tangentiallinie at the leading edge. Depending on the relative degree of steepness of two adjacently arranged blades, the position of the narrowest cross-sectional area T migrates along the blade surface. On the pressure side, the narrowest cross-sectional area T intersects the corresponding guide blade in each case in the region of the blade inlet edge, while on the suction side the intersection line of the narrowest cross-sectional area with the respective guide blade can sometimes move all the way to the end of the guide blade. In the embodiment according to FIG. 3, the respective relative degree of steepness between two guide vanes of a group is relatively constant due to the constant angular spacing, that is to say the respective relative angular position is approximately constant. Deviating angular positions, however, result in the transitional region of the two groups. Further, not shown embodiments are also possible. In this case, for example, all angular distances of the guide vanes can be identical except for one or a few. It can be formed more than two groups, each with identical angular intervals. These pairs of vanes with identical angular intervals may be arranged in a row or separated from each other. Optionally, the individual vanes of the diffuser may differ in shape, length, entry and exit angles, and entry and exit radii, to introduce additional inequalities into the diffuser. The different training can be done both in the axial direction (with respect to the compressor axis), ie in the direction of the blade height, as well as in the circumferential direction. In this case, all or only a few guide vanes can be shaped or arranged differently. Such irregularly formed diffusers may be formed in one or more stages, with several stages arranged in the radial direction one behind the other, ie concentrically with respect to the compressor axis. According to the invention, in all these embodiments, the narrowest cross-sectional area in the diffuser channel between two vanes and above the diffuser channel height is constant. If the diffuser has a variable, ie non-constant, diffuser channel height distributed over the circumference, the guide vanes are to be arranged in accordance with the invention so that the narrowest cross-sectional area calculated from the spacing between the adjacent guide vanes and the diffuser channel height is constant.
Optional lässt sich der in Umfangsrichtung unregelmässig ausgebildete Diffusor bezüglich des in Umfangsrichtung asymmetrisch ausgebildeten Spiralgehäuses in einer fixen Winkellage positioniert. Dadurch kann die Grösse der unterschiedlichen Winkelabstände sowie deren Verteilung entlang dem Umfang auf das asymmetrisch ausgebildete Spiralgehäuse stromab der Leitschaufeln ausgerichtet werden. Die Winkelabstände können beispielsweise entlang dem Umfang analog zum Radius des Spiralgehäuses zunehmen. Oder dasjenige Leitschaufelpaar, welches im Bereich des Spiralzungenanfangs angeordnet ist, kann einen von den übrigen Leitschaufelpaaren unterschiedlichen Winkelabstand aufweisen. Optionally, the irregularly formed in the circumferential direction diffuser can be positioned with respect to the circumferentially asymmetric spiral housing in a fixed angular position. As a result, the size of the different angular distances and their distribution along the circumference can be aligned with the asymmetrically formed volute casing downstream of the guide vanes. The angular distances can increase, for example, along the circumference analogous to the radius of the spiral housing. Or that Leitschaufelpaar, which is arranged in the region of the Spiralzungenanfangs, may have a different angular distance from the other Leitschaufelpaaren.
Da sich das Spiralgehäuse 31 üblicherweise entlang des Umfangs in unterschiedlichen Winkellagen zum Lagergehäuse positionieren lässt, wird erfindungsgemäss mit Positionierungsmitteln sichergestellt, dass sich der Diffusor jeweils in der vorgesehenen Winkellage zum Spiralgehäuse befindet. Die vorgesehene Winkellage ist dabei vorteilhafterweise diejenige, bei welcher im Betrieb eine minimale Resonanzschwingung erzeugt wird. Diese Winkellage von Diffusor zum Spiralgehäuse mit minimaler Resonanzschwingungserzeugung kann optional errechnet oder experimentell bestimmt werden. Ein mögliches Positionierungsmittel ist in Fig. 2 angedeutet, mit einem Positionierungsnocken 23 an dem radial äusseren Rand der Diffusorwand 22, welcher in einer Positionierungsnut 33 im Spiralgehäuse eingreift. Andere formschlüssige Positionierungsmittel sind denkbar, etwa ein Positionierungsstift, welcher in beidseitig eingelassenen Bohrungen angeordnet ist. Auch die indirekte Positionierung über ein drittes Bauteil, etwa das Eintrittsgehäuse 32 oder das Lagergehäuse 30 sind denkbar. Bezugszeichenliste Since the spiral housing 31 can usually be positioned along the circumference in different angular positions relative to the bearing housing, according to the invention positioning means ensure that the diffuser is in each case in the intended angular position relative to the spiral housing. The envisaged angular position is advantageously the one in which a minimum resonance oscillation is generated during operation. This angular position from diffuser to volute with minimal resonant vibration generation can optionally be calculated or determined experimentally. A possible positioning means is indicated in Fig. 2, with a positioning cam 23 on the radially outer edge of the diffuser wall 22, which engages in a positioning groove 33 in the spiral housing. Other positive positioning means are conceivable, such as a positioning pin, which is arranged in recesses bored on both sides. The indirect positioning via a third component, such as the inlet housing 32 or the bearing housing 30 are conceivable. LIST OF REFERENCE NUMBERS
10 Verdichterrad (Nabe)  10 compressor wheel (hub)
1 1 Laufschaufeln des Verdichterrades  1 1 blades of the compressor wheel
12 Welle  12 wave
21 , 210, 21 1 Leitschaufeln des Diffusors  21, 210, 21 1 Guide vanes of the diffuser
22 Wand des Diffusors  22 wall of the diffuser
23 Positionierungsnocken  23 positioning cams
30 Lagergehäuse  30 bearing housing
31 Spiralgehäuse  31 spiral housing
32 Eintrittsgehäuse  32 inlet housing
33 Positionierungsnut  33 positioning groove
dx Winkelabstand zwischen zwei Diffusor-Leitschaufeln ßA Relative Winkellage der Diffusor-Leitschaufel dx Angular distance between two diffuser vanes ßA Relative angular position of the diffuser vane
T Engste Querschnittsfläche zwischen zwei Leitschaufeln  T Narrow cross-sectional area between two vanes

Claims

P AT E N TA N S P R Ü C H E P AT E N TA N S P R O C H E
Beschaufeiter Diffusor eines Radialverdichters, mit mehreren, in Umfangsrichtung verteilt angeordneten Leitschaufeln (21 ) wobei sich der Winkelabstand (ao) zweier benachbart zueinander angeordneter Leitschaufeln (21 ) unterscheidet vom Winkelabstand (CM , ci2, 03) zweier anderer benachbart zueinander angeordneter Leitschaufeln (21 ), dadurch gekennzeichnet, dass die über den Umfang verteilten Leitschaufeln (21 ) teilweise voneinander abweichende relative Winkellagen (ßo, ßi, ß2, ß3) aufweisen, so dass eine engste Querschnittsfläche (T) des Diffusor-Kanals, welcher von zwei benachbart zueinander angeordneten Leitschaufeln begrenzt ist, für alle von zwei benachbart zueinander angeordneten Leitelement-Paarungen begrenzten Diffusor-Kanäle gleich gross ist.  A contoured diffuser of a radial compressor, comprising a plurality of circumferentially distributed vanes (21), the angular spacing (ao) of two adjacent vanes (21) being different from the angular separation (CM, ci2, 03) of two other vanes (21) arranged adjacent to each other , characterized in that the circumferentially distributed vanes (21) partially differing relative angular positions (ßo, ßi, ß2, ß3), so that a narrowest cross-sectional area (T) of the diffuser channel, which of two adjacently arranged vanes is limited, for all of two adjacent to each other arranged Leitelement pairings limited diffuser channels is the same size.
Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 1 , wobei mehrere Paare von jeweils benachbart zueinander angeordneten Leitschaufeln (21 ) einen anderen Winkelabstand aufweisen als die übrigen, jeweils benachbart zueinander angeordneten Leitschaufeln. The contoured diffuser of a centrifugal compressor according to claim 1, wherein a plurality of pairs of respective adjacent vanes (21) have a different angular spacing than the remaining vanes respectively arranged adjacent to each other.
Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 2, wobei mindestens zwei Paare von jeweils benachbart zueinander angeordneten Leitschaufeln einen ersten Winkelabstand (ao) aufweisen und zumindest zwei andere Paare von jeweils benachbart zueinander angeordneten Leitschaufeln einen, vom ersten verschiedenen, zweiten Winkelabstand (αι) aufweisen. 2. The contoured diffuser of a centrifugal compressor according to claim 2, wherein at least two pairs of respective adjacent vanes have a first angular distance and at least two other pairs of vanes adjacent to each other have a second angular distance different from the first.
Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 3, wobei mehrere Paare von jeweils benachbart zueinander angeordneten Leitschaufeln jeweils den gleichen Winkelabstand (ao, ai) aufweisen. A contoured diffuser of a centrifugal compressor according to claim 3, wherein a plurality of pairs of respective adjacent vanes each having the same angular distance (ao, ai).
Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 4, wobei die Leitschaufeln in mehrere Gruppen aufgeteilt sind, mit jeweils gleichen Winkelabständen (ao, ai) zwischen den benachbart zueinander angeordneten Leitschaufeln einer Gruppe. A contoured diffuser of a centrifugal compressor according to claim 4, wherein the guide vanes are divided into a plurality of groups, each having equal angular intervals (ao, ai) between the adjacent vanes of a group.
Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 5, wobei die Leitschaufeln in zwei Gruppen aufgeteilt sind, eine der Gruppen eine Leitschaufel mehr aufweist als die andere Gruppe, und beide Gruppen von Leitschaufeln jeweils über die Hälfte des Umfangs verteilt angeordnet sind. A contoured diffuser of a centrifugal compressor according to claim 5, wherein the vanes are divided into two groups, one of the groups has one vane more than the other group, and both groups of vanes are distributed over half of the circumference, respectively.
7. Beschaufeiter Diffusor eines Radialverdichters nach Anspruch 2, wobei jedes Paar von benachbart zueinander angeordneten Leitschaufeln einen anderen Winkelabstand aufweist als die übrigen, jeweils benachbart zueinander angeordneten Leitschaufeln. 8. Abströmbereich eines Radialverdichters, umfassend ein in Umfangsrichtung asymmetrisch ausgebildetes und in Umfangsrichtung in verschiedenen Winkellagen positionierbares Spiralgehäuse (31 ) sowie einen beschaufelten Diffusor nach einem der Ansprüche 1 bis 7. A composite radial diffuser according to claim 2, wherein each pair of adjacent vanes are at a different angular spacing than the remaining vanes adjacent to each other. 8. outflow region of a radial compressor, comprising a circumferentially asymmetric trained and circumferentially positionable in different angular positions spiral housing (31) and a bladed diffuser according to one of claims 1 to 7.
9. Abströmbereich eines Radialverdichters nach Anspruch 8, wobei am Spiralgehäuse (31 ) und am Diffusor Positionierungsmittel (33, 23) zur definierten Winkellage des9. discharge area of a radial compressor according to claim 8, wherein the spiral housing (31) and the diffuser positioning means (33, 23) for the defined angular position of the
Diffusors bezüglich des Spiralgehäuses vorgesehen sind. Diffusers are provided with respect to the spiral housing.
10. Abgasturbolader, gekennzeichnet durch einen Radialverdichter mit einem Abströmbereich nach einem der vorangehenden Ansprüche. 10. Exhaust gas turbocharger, characterized by a centrifugal compressor with a discharge area according to one of the preceding claims.
EP15730184.7A 2014-06-24 2015-06-22 Diffuser for a radial compressor Withdrawn EP3161325A1 (en)

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CN114846245A (en) * 2020-01-23 2022-08-02 诺沃皮尼奥内技术股份有限公司 Return channel with non-constant return channel blade pitch and centrifugal turbomachine comprising said return channel
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