EP1233190B1 - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

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Publication number
EP1233190B1
EP1233190B1 EP02003087A EP02003087A EP1233190B1 EP 1233190 B1 EP1233190 B1 EP 1233190B1 EP 02003087 A EP02003087 A EP 02003087A EP 02003087 A EP02003087 A EP 02003087A EP 1233190 B1 EP1233190 B1 EP 1233190B1
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EP
European Patent Office
Prior art keywords
housing
compressor
spiral
radial direction
bearing housing
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EP02003087A
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German (de)
French (fr)
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EP1233190A1 (en
Inventor
Dr. Klaus Bartholomä
Wolfgang Schmidt
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MAN Energy Solutions SE
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MAN Diesel and Turbo SE
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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—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
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/10—Geometry two-dimensional
    • F05B2250/15—Geometry two-dimensional spiral
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/20—Geometry three-dimensional
    • F05B2250/25—Geometry three-dimensional helical
    • 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

Definitions

  • the invention relates to a centrifugal compressor with a compressor wheel, which is enclosed by a spiral compressor housing with a helical flow channel, according to the preamble of patent claim 1.
  • Smaller turbochargers can absorb these forces due to the relatively large wall thicknesses and the rigid housing parts.
  • the housing wall thicknesses are usually reduced for casting reasons, whereby at such stress, the breaking point of the material is reached quickly and it can lead to housing breaks. It may leak fragments from the turbocharger, with considerable consequential damage.
  • the compressor housing an outer spiral housing, which comprises the radially outwardly deflected in the channel portion of the flow channel, and an inner Genosusprin lake which is provided in the radial direction between the volute casing and the compressor wheel and its inner contour with the outer contour of the hub of the compressor wheel the substantially extending in the axial direction channel portion of the flow channel, has, the spiral housing is designed with a housing insert at least partially surrounding inner cylinder to which the Genosusschreibrios is grown to form a cavity by means of a flexible fixation in the axial direction, and the flexible fixation of the Housing insert less unbreakable than the rigid fixation of the compressor housing is carried out on the bearing housing, a spiral housing has been formed with a "crumple zone" from this no fragment of a ruptured L. alsrades can escape more. The kinetic energy of fragments of a bursting compressor wheel can now be fully converted into deformation energy and heat within the turbocharger.
  • An additional burst protection outside the spiral housing can be omitted.
  • volute casing is designed with an inner cylinder at least partially surrounding the inner cylinder, on which the Gepatiusprin committee is grown to form a cavity by means of a flexible fixation in the axial direction, high protection against destruction of the volute casing itself is ensured and an effective "brake” given against leakage of debris from the turbocharger.
  • the intended for rigid fixation of the volute casing wall of the bearing housing in the radial direction is arranged pulled down over the outer tip of the outer contour of the compressor wheel to form a gap, so that an additional "brake”, ie securing against a radial escape of Fragments of the compressor wheel is specified.
  • a further particularly advantageous embodiment is the fact that the compressor housing is attached to the bearing housing via the outer spiral housing so as to form a parting line that the outer, the deflected channel section comprising volute to the rigid fixation of the compressor housing on the bearing housing over in the radial direction B to is pulled inside, so that the rigid fixation in the radial direction B is further outwardly disposed as the parting line between spiral and bearing housing.
  • This measure of the special arrangement of the parting line ensures that the rigid fixation of the compressor housing on the bearing housing is hardly burdened by any wedged in the flow channel fragments, whereby a breaking away of the compressor housing is further excluded.
  • the exhaust gas turbocharger of the type underlying in the drawing has a mounted in its central longitudinal region in a bearing housing shaft 1 2, which carries a not shown here turbine wheel and a schematically shown in the drawing radially flowed compressor wheel 3 at their projecting over the bearing ends.
  • the illustrated compressor wheel 3 has a hub 4 which is rotationally received on the shaft 2 driven by the turbine wheel and which is circumferentially occupied by radially projecting blades 5.
  • the outer contour 6 of the hub 4 bounded with the inner contour 7 of a compressor housing 8 a deflected from the axial direction A in the radial direction B, outwardly narrowing flow channel 9, whose cross section corresponds to the configuration of the blades 5.
  • the compressor housing 8 is fixed by means of a rigid fixation 18 on the bearing housing 1.
  • the diameter of the hub 4 and the blades 5 increases from the flow inlet to the flow outlet, so that a symmetrical to the median transverse plane of the compressor 3 longitudinal cross-section and, accordingly, over the length of the compressor 3 increasing mass distribution arise.
  • the compressor housing 8 is made of an outer fixed to the bearing housing by means of the rigid fixation 18 spiral housing 10, which comprises the outwardly deflected in the radial direction B channel portion 11 of the flow channel 9, and an inner Gepatiusprin Federation 12, in the radial direction B between the volute 10th and the compressor wheel 3 is provided and its inner contour 13 with the outer contour 6 of the hub 4 of the compressor wheel third forms the substantially extending in the axial direction A channel portion 14 of the flow channel 9, constructed.
  • the compressor housing 8 is attached via the outer volute casing 10 so as to form a parting line 22 on the bearing housing 1, that the outer, the deflected channel section 11 comprehensive volute 10 to the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 over in the radial direction B inward is pulled, so that the rigid fixation 18 in the radial direction B further outwardly lying as the parting line 22 between the spiral-10 and bearing housing 1 is arranged.
  • This measure of the special arrangement of the parting line 22 ensures that the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 is hardly burdened by any wedged in the flow channel 9 fragments, whereby a breaking away of the compressor housing 8 is further excluded.
  • the distance between the parting line 22 and the shaft 2 is smaller than the distance of the surface center 23 of the largest cross-sectional area 24 by the deflected channel portion 11 in the volute 10 to the shaft second
  • the spiral housing 10 is designed with an inner cylinder 15 at least partially surrounding the housing insert piece 12, on which the housing insert piece 12 is mounted to form a cavity 16 by means of a flexible fixing 17 in the axial direction A.
  • the flexible fixing 17 of the housing insert 12 is significantly less unbreakable than the rigid fixation 18 of the spiral housing 10 on the bearing housing 1 executed.
  • the rigid fixation 18 of the compressor housing 8, or the spiral housing 10 is by means of a fixed flange of the volute casing 10 on the bearing housing 1 and the flexible fixing 17 of the housing insert 12 by means of a Dehnschraubenfix ist in the axial direction A performed by the inner cylinder 15 of the spiral housing 10.
  • the intended for rigid fixation 18 of the volute 8 wall 19 of the bearing housing 1 is arranged in the radial direction B pulled down over the outer tip 20 of the outer contour 6 of the hub 4 of the compressor wheel 3 to form a gap 21.
  • the spiral housing 10 is designed with the diameter of the flow channel 9 becoming smaller and smaller towards the inside in the direction of the compressor wheel 3.

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

Description

Die Erfindung betrifft einen Radialverdichter mit einem Verdichterrad, das von einem spiralförmigen Verdichtergehäuse mit einem schneckenförmigen Strömungskanal umschlossen ist, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a centrifugal compressor with a compressor wheel, which is enclosed by a spiral compressor housing with a helical flow channel, according to the preamble of patent claim 1.

Der grundsätzliche Aufbau und die Wirkungsweise derartiger Radialverdichter z.B. eines Turboladers, sind an sich bekannt und bedürfen daher im vorliegenden Zusammenhang keiner näheren Erläuterung mehr. So ist beispielsweise in der DE 195 02 808 C2 , die als nächstliegender Stand der Technik angesehen wird, ein gattungsbildende Radialverdichter eines Turboladers beschrieben, innerhalb dessen spiralförmigen Verdichtergehäuse der Durchmesser der Nabe des Verdichterrades und der Schaufeln in Strömungsrichtung zunimmt und die Aussenkontur der Schaufeln bogenförmig ist' und der Innenkontur der benachbarten, torusförmig nach aussen gekrümmten Kanalwand des schneckenförmigen Strömungskanals entspricht, wobei die Kanalwand des Verdichtergehäuses mit der Aussenkontur der Nabe des Verdichterrades einen nach aussen umgelenkten Kanalabschnitt begrenzen, in diesen die Schaufeln eingreifen. An diesen nach aussen radial umgelenkten Kanalabschnitt schliesst sich ein in einen Spiralkanal einmündender ringförmiger Kanalabschnitt an.The basic structure and the operation of such radial compressor, for example a turbocharger, are known per se and therefore need no further explanation in the present context. For example, in the DE 195 02 808 C2 , which is considered to represent the closest prior art, describes a generic radial compressor of a turbocharger within which spiral compressor housing the diameter of the hub of the compressor wheel and the blades increases in the flow direction and the outer contour of the blades is arcuate 'and the inner contour of the adjacent, toroidal outwardly curved channel wall of the helical flow channel corresponds, wherein the channel wall of the compressor housing with the outer contour of the hub of the compressor wheel define an outwardly deflected channel section in which the blades engage. At this outwardly radially deflected channel section is followed by an opening into a spiral channel annular channel section.

Üblicherweise werden derartige Verdichtergehäuse von Turboladern und deren Einbauten starr ausgeführt.Usually, such compressor housing of turbochargers and their internals are rigid.

Nach langem Betrieb unter ungünstigen Bedingungen kann ein derartiges Verdichterrad durch Korrosion, Erosion und Alterung so stark geschwächt werden, dass das Bersten des Verdichterrades nicht ausgeschlossen werden kann. Im Falle eines Verdichterradbruches, bei dem das Rad meistens in zwei oder drei grosse Teilstücke zerbricht, werden diese Einzelteile durch die erheblichen Zentrifugalkräfte nach aussen geschleudert. Es können dann sogar Bruchstücke aus dem Verdichtergehäuse austreten. Dabei werden die Verdichterradschaufeln völlig zerstört und der verbleibende Nabenkörper verklemmt sich zwischen dem Lagergehäuse und dem Verdichtergehäuse. Durch die Formgebung der Nabenstücke entsteht dabei eine Keilwirkung, die erhebliche impulsartige Axialkräfte auf die Gehäuse ausüben.After a long period of operation under unfavorable conditions, such a compressor wheel can be so greatly weakened by corrosion, erosion and aging. that the bursting of the compressor wheel can not be excluded. In the case of a Verdichterradbruches, in which the wheel usually breaks into two or three large sections, these items are thrown by the significant centrifugal forces to the outside. It can even escape fragments from the compressor housing. The compressor wheel blades are completely destroyed and the remaining hub body jammed between the bearing housing and the compressor housing. The shape of the hub pieces creates a wedge effect, which exert considerable momentum-like axial forces on the housing.

Kleinere Turbolader können durch die relativ grossen Wandstärken und die steifen Gehäuseteile diese Kräfte aufnehmen. Bei grossen Turboladern werden die Gehäusewandstärken meist aus giesstechnischen Gründen verringert, wodurch bei derartiger Beanspruchung die Bruchgrenze des Materials schnell erreicht wird und es zu Gehäusebrüchen kommen kann. Dabei können Bruchstücke aus dem Turbolader austreten, mit erheblichen Folgeschäden.Smaller turbochargers can absorb these forces due to the relatively large wall thicknesses and the rigid housing parts. In large turbochargers, the housing wall thicknesses are usually reduced for casting reasons, whereby at such stress, the breaking point of the material is reached quickly and it can lead to housing breaks. It may leak fragments from the turbocharger, with considerable consequential damage.

Dies sollte unbedingt vermieden werden. Zu diesem Zwecke ist es heute üblich, ausserhalb des das Verdichterrad aufnehmenden Verdichtergehäuses einen zusätzlichen Berstschutz vorzusehen.This should be avoided at all costs. For this purpose, it is common today to provide an additional bursting protection outside of the compressor housing receiving the compressor.

Hiervon ausgehend ist es daher die Aufgabe der vorliegenden Erfindung, eine Strömungsmaschine eingangs erwähnter Art mit einfachen und kostengünstigen Mitteln so weiterzubilden, dass das Austreten von Bruchstücken eines geborstenen Verdichterrades aus dem Verdichtergehäuse verhindert werden kann, ohne einen zusätzlichen Berstschutz ausserhalb des Spiralgehäuses. vorsehen zu müssen.On this basis, it is therefore an object of the present invention to develop a fluid flow machine of the type mentioned with simple and inexpensive means so that the escape of fragments of a ruptured compressor wheel can be prevented from the compressor housing, without an additional burst protection outside the spiral housing. to have to provide.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This object is achieved by the characterizing features of claim 1.

Dadurch, dass das Verdichtergehäuse ein äusseres Spiralgehäuse, das den in die radiale Richtung nach aussen umgelenkten Kanalabschnitt des Strömungskanals umfasst, und ein inneres Gehäuseeinsatzstück, das in radialer Richtung zwischen dem Spiralgehäuse und dem Verdichterrad vorgesehen ist und dessen Innenkontur mit der Aussenkontur der Nabe des Verdichterrades den im wesentlichen in axialer Richtung verlaufenden Kanalabschnitt des Strömungskanals ausbildet, aufweist, das Spiralgehäuse mit einem das Gehäuseeinsatzstück zumindest teilweise umgebenden Innenzylinder ausgeführt ist, an diesem das Gehäuseeinsatzstück zur Ausbildung eines Hohlraumes mittels einer in axialer Richtung flexiblen Fixierung angebaut ist, und die flexible Fixierung des Gehäuseeinsatzes weniger bruchsicher als die starre Fixierung des Verdichtergehäuses am Lagergehäuse ausgeführt ist, ist ein Spiralgehäuse mit einer "Knautschzone" ausgebildet worden, aus diesem kein Bruchstück eines geborstenen Laufrades mehr austreten kann. Die kinetische Energie von Bruchstücken eines berstenden Verdichterrades kann nun innerhalb des Turboladers vollständig in Verformungsenergie und Wärme umgewandelt werden.Characterized in that the compressor housing an outer spiral housing, which comprises the radially outwardly deflected in the channel portion of the flow channel, and an inner Gehäuseinsatzstück which is provided in the radial direction between the volute casing and the compressor wheel and its inner contour with the outer contour of the hub of the compressor wheel the substantially extending in the axial direction channel portion of the flow channel, has, the spiral housing is designed with a housing insert at least partially surrounding inner cylinder to which the Gehäuseinsatzstück is grown to form a cavity by means of a flexible fixation in the axial direction, and the flexible fixation of the Housing insert less unbreakable than the rigid fixation of the compressor housing is carried out on the bearing housing, a spiral housing has been formed with a "crumple zone" from this no fragment of a ruptured L. aufrades can escape more. The kinetic energy of fragments of a bursting compressor wheel can now be fully converted into deformation energy and heat within the turbocharger.

Dadurch, dass die starre Fixierung des Spiralgehäuses am Lagergehäuse, sowie das Gehäuseeinsatzstück selbst deutlich mehr kinetische Energie als die flexible Fixierung des Gehäuseeinsatzstückes am Spiralgehäuse aufnehmen kann, ist gewährleistet, dass das Gehäuseeinsatzstück sich im Notfall in axialer Richtung vom Verdichterrad wegbewegen kann. So kann die kinetische Energie der Verdichterradstücke durch Umwandlung in Verformungsenergie und daraus resultierender Wärme zum grossen Teil aufgenommen werden. Die verbleibende kinetische Energie der Bruchstücke kann von den Gehäusen aufgenommen werden.The fact that the rigid fixation of the spiral housing on the bearing housing, and the housing insert itself can absorb much more kinetic energy than the flexible fixation of the housing insert on the volute, it is ensured that the housing insert can move away in an emergency in the axial direction of the compressor. Thus, the kinetic energy of the compressor wheel pieces can be largely absorbed by conversion to deformation energy and resulting heat. The remaining kinetic energy of the debris can be absorbed by the housings.

Ein zusätzlicher Berstschutz ausserhalb des Spiralgehäuses kann entfallen.An additional burst protection outside the spiral housing can be omitted.

Dadurch, dass das Spiralgehäuse mit einem das Gehäuseeinsatzstück zumindest teilweise umgebenden Innenzylinder ausgeführt ist, an diesem das Gehäuseeinsatzstück zur Ausbildung eines Hohlraumes mittels einer in axialer Richtung flexiblen Fixierung angebaut ist, ist ein hoher Schutz vor Zerschlagung des Spiralgehäuses selbst sichergestellt und eine wirksame "Bremse" gegen ein Austreten von Bruchstücken aus dem Turbolader gegeben. Erfindungsgemäß ist die starre Fixierung des Verdichtergehäuses mittels einer festen Flanschverbindung des Spiralgehäuses am Lagergehäuse und die flexible Fixierung des Gehäuseeinsatzstückes mittels einer Dehnschraubenfixierung in axialer Richtung durch den Innenzylinder des Spiralgehäuses ausgeführt.Characterized in that the volute casing is designed with an inner cylinder at least partially surrounding the inner cylinder, on which the Gehäuseinsatzstück is grown to form a cavity by means of a flexible fixation in the axial direction, high protection against destruction of the volute casing itself is ensured and an effective "brake" given against leakage of debris from the turbocharger. According to the invention, the rigid fixation of the compressor housing by means of a fixed flange of the volute casing on the bearing housing and the flexible fixation of the housing insert piece by means of a Dehnschraubenfixierung in the axial direction by the inner cylinder of the spiral housing.

In besonders vorteilhafter Weise ist die zur starren Fixierung des Spiralgehäuses vorgesehene Wand des Lagergehäuses in radialer Richtung bis über die äussere Spitze der Aussenkontur des Verdichterrades unter Ausbildung eines Spaltes heruntergezogen angeordnet, so dass eine zusätzliche "Bremse", das heisst Sicherung gegen ein radiales Austreten von Bruchstücken des Verdichterrades vorgegeben ist.In a particularly advantageous manner, the intended for rigid fixation of the volute casing wall of the bearing housing in the radial direction is arranged pulled down over the outer tip of the outer contour of the compressor wheel to form a gap, so that an additional "brake", ie securing against a radial escape of Fragments of the compressor wheel is specified.

Eine weitere besonders vorteilhafte Ausbildung ist darin zu sehen, dass das Verdichtergehäuse über das äussere Spiralgehäuse derart unter Ausbildung einer Trennfuge am Lagergehäuse angesetzt ist, dass das äussere, den umgelenkten Kanalabschnitt umfassende Spiralgehäuse an der starren Fixierung des Verdichtergehäuses am Lagergehäuse vorbei in radialer Richtung B nach innen gezogen ist, so dass die starre Fixierung in radialer Richtung B weiter aussen liegend als die Trennfuge zwischen Spiral- und Lagergehäuse angeordnet ist. Diese Massnahme der besonderen Anordnung der Trennfuge stellt sicher, dass die starre Fixierung des Verdichtergehäuses am Lagergehäuse von eventuell sich im Strömungskanal verkeilenden Bruchstücken kaum belastet wird, wodurch ein Wegbrechen des Verdichtergehäuses noch weiter ausgeschlossen wird.A further particularly advantageous embodiment is the fact that the compressor housing is attached to the bearing housing via the outer spiral housing so as to form a parting line that the outer, the deflected channel section comprising volute to the rigid fixation of the compressor housing on the bearing housing over in the radial direction B to is pulled inside, so that the rigid fixation in the radial direction B is further outwardly disposed as the parting line between spiral and bearing housing. This measure of the special arrangement of the parting line ensures that the rigid fixation of the compressor housing on the bearing housing is hardly burdened by any wedged in the flow channel fragments, whereby a breaking away of the compressor housing is further excluded.

Die Erfindung soll nachfolgend aus einer Beispielsbeschreibung anhand der Zeichnung näher erläutert werden.The invention will be explained in more detail below from an example description with reference to the drawing.

Die nachstehend beschriebene Zeichnung zeigt einen Teillängsschnitt durch eine erfindungsgemässe Strömungsmaschine in Form eines Radialverdichters.The drawing described below shows a partial longitudinal section through an inventive flow machine in the form of a centrifugal compressor.

Der Abgasturbolader der in der Zeichnung zugrundeliegenden Art besitzt eine in ihrem mittleren Längsbereich in einem Lagergehäuse 1 gelagerte Welle 2, die an ihren über die Lagerung auskragenden Enden ein hier nicht dargestelltes Turbinenrad und ein in der Zeichnung schematisch dargestelltes radial durchströmtes Verdichterrad 3 trägt.The exhaust gas turbocharger of the type underlying in the drawing has a mounted in its central longitudinal region in a bearing housing shaft 1 2, which carries a not shown here turbine wheel and a schematically shown in the drawing radially flowed compressor wheel 3 at their projecting over the bearing ends.

Das dargestellte Verdichterrad 3 besitzt eine auf der durch das Turbinenrad angetriebenen Welle 2 drehschlüssig aufgenommene Nabe 4, die umfangsseitig mit radial abstehenden Schaufeln 5 besetzt ist. Die Aussenkontur 6 der Nabe 4 begrenzt mit der Innenkontur 7 eines Verdichtergehäuses 8 einen von der axialen Richtung A in die radiale Richtung B umgelenkten, nach aussen sich verengenden Strömungskanal 9, dessen Querschnitt der Konfiguration der Schaufeln 5 entspricht. Das Verdichtergehäuse 8 ist mittels einer starren Fixierung 18 am Lagergehäuse 1 befestigt. Der Durchmesser der Nabe 4 und der Schaufeln 5 nimmt vom Strömungseingang zum Strömungsausgang zu, so dass sich ein zur Mittelquerebene des Verdichterrads 3 unsymmetrischer Längsquerschnitt und dementsprechend auch eine über der Länge des Verdichterrads 3 zunehmende Masseverteilung ergeben.The illustrated compressor wheel 3 has a hub 4 which is rotationally received on the shaft 2 driven by the turbine wheel and which is circumferentially occupied by radially projecting blades 5. The outer contour 6 of the hub 4 bounded with the inner contour 7 of a compressor housing 8 a deflected from the axial direction A in the radial direction B, outwardly narrowing flow channel 9, whose cross section corresponds to the configuration of the blades 5. The compressor housing 8 is fixed by means of a rigid fixation 18 on the bearing housing 1. The diameter of the hub 4 and the blades 5 increases from the flow inlet to the flow outlet, so that a symmetrical to the median transverse plane of the compressor 3 longitudinal cross-section and, accordingly, over the length of the compressor 3 increasing mass distribution arise.

Das Verdichtergehäuse 8 ist aus einem äusseren am Lagergehäuse mittels der starren Fixierung 18 festgemachten Spiralgehäuse 10, das den in die radiale Richtung B nach aussen umgelenkten Kanalabschnitt 11 des Strömungskanals 9 umfasst, und einem inneren Gehäuseeinsatzstück 12, das in radialer Richtung B zwischen dem Spiralgehäuse 10 und dem Verdichterrad 3 vorgesehen ist und dessen Innenkontur 13 mit der Aussenkontur 6 der Nabe 4 des Verdichterrades 3 den im wesentlichen in axialer Richtung A verlaufenden Kanalabschnitt 14 des Strömungskanals 9 ausbildet, aufgebaut.The compressor housing 8 is made of an outer fixed to the bearing housing by means of the rigid fixation 18 spiral housing 10, which comprises the outwardly deflected in the radial direction B channel portion 11 of the flow channel 9, and an inner Gehäuseinsatzstück 12, in the radial direction B between the volute 10th and the compressor wheel 3 is provided and its inner contour 13 with the outer contour 6 of the hub 4 of the compressor wheel third forms the substantially extending in the axial direction A channel portion 14 of the flow channel 9, constructed.

Das Verdichtergehäuse 8 ist über das äussere Spiralgehäuse 10 derart unter Ausbildung einer Trennfuge 22 am Lagergehäuse 1 angesetzt ist, dass das äussere, den umgelenkten Kanalabschnitt 11 umfassende Spiralgehäuse 10 an der starren Fixierung 18 des Verdichtergehäuses 8 am Lagergehäuse 1 vorbei in radialer Richtung B nach innen gezogen ist, so dass die starre Fixierung 18 in radialer Richtung B weiter aussen liegend als die Trennfuge 22 zwischen Spiral-10 und Lagergehäuse 1 angeordnet ist. Diese Massnahme der besonderen Anordnung der Trennfuge 22 stellt sicher, dass die starre Fixierung 18 des Verdichtergehäuses 8 am Lagergehäuse 1 von eventuell sich im Strömungskanal 9 verkeilenden Bruchstücken kaum belastet wird, wodurch ein Wegbrechen des Verdichtergehäuses 8 noch weiter ausgeschlossen wird.The compressor housing 8 is attached via the outer volute casing 10 so as to form a parting line 22 on the bearing housing 1, that the outer, the deflected channel section 11 comprehensive volute 10 to the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 over in the radial direction B inward is pulled, so that the rigid fixation 18 in the radial direction B further outwardly lying as the parting line 22 between the spiral-10 and bearing housing 1 is arranged. This measure of the special arrangement of the parting line 22 ensures that the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 is hardly burdened by any wedged in the flow channel 9 fragments, whereby a breaking away of the compressor housing 8 is further excluded.

In bevorzugter Weise ist beim Ausführungsbeispiel der Abstand zwischen der Trennfuge 22 und der Welle 2 kleiner als der Abstand des Flächenmittelpunktes 23 der grössten Querschnittsfläche 24 durch den umgelenkten Kanalabschnitt 11 im Spiralgehäuse 10 zur Welle 2.Preferably, in the embodiment, the distance between the parting line 22 and the shaft 2 is smaller than the distance of the surface center 23 of the largest cross-sectional area 24 by the deflected channel portion 11 in the volute 10 to the shaft second

Das Spiralgehäuse 10 ist mit einem das Gehäuseeinsatzstück 12 zumindest teilweise umgebenden Innenzylinder 15 ausgeführt, an diesem das Gehäuseeinsatzstück 12 zur Ausbildung eines Hohlraumes 16 mittels einer in axialer Richtung A flexiblen Fixierung 17 angebaut ist. Die flexible Fixierung 17 des Gehäuseeinsatzes 12 ist deutlich weniger bruchsicher als die starre Fixierung 18 des Spiralgehäuses 10 am Lagergehäuse 1 ausgeführt.The spiral housing 10 is designed with an inner cylinder 15 at least partially surrounding the housing insert piece 12, on which the housing insert piece 12 is mounted to form a cavity 16 by means of a flexible fixing 17 in the axial direction A. The flexible fixing 17 of the housing insert 12 is significantly less unbreakable than the rigid fixation 18 of the spiral housing 10 on the bearing housing 1 executed.

Die starre Fixierung 18 des Verdichtergehäuses 8, bzw. des Spiralgehäuses 10 ist mittels einer festen Flanschverbindung des Spiralgehäuses 10 am Lagergehäuse 1 und die flexible Fixierung 17 des Gehäuseeinsatzstückes 12 mittels einer Dehnschraubenfixierung in axialer Richtung A durch den Innenzylinder 15 des Spiralgehäuses 10 ausgeführt.The rigid fixation 18 of the compressor housing 8, or the spiral housing 10 is by means of a fixed flange of the volute casing 10 on the bearing housing 1 and the flexible fixing 17 of the housing insert 12 by means of a Dehnschraubenfixierung in the axial direction A performed by the inner cylinder 15 of the spiral housing 10.

Die zur starren Fixierung 18 des Spiralgehäuses 8 vorgesehene Wand 19 des Lagergehäuses 1 ist in radialer Richtung B bis über die äussere Spitze 20 der Aussenkontur 6 der Nabe 4 des Verdichterrades 3 unter Ausbildung eines Spaltes 21 heruntergezogen angeordnet.The intended for rigid fixation 18 of the volute 8 wall 19 of the bearing housing 1 is arranged in the radial direction B pulled down over the outer tip 20 of the outer contour 6 of the hub 4 of the compressor wheel 3 to form a gap 21.

Das Spiralgehäuse 10 ist mit nach innen in Richtung des Verdichterrades 3 immer kleiner werdenden Durchmesser des Strömungskanals 9 ausgeführt.The spiral housing 10 is designed with the diameter of the flow channel 9 becoming smaller and smaller towards the inside in the direction of the compressor wheel 3.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Lagergehäusebearing housing
22
Wellewave
33
Verdichterradcompressor
44
Nabehub
55
Schaufelnshovel
66
Aussenkontur der NabeOuter contour of the hub
77
Innenkontur von 8 und 12Inner contour of 8 and 12
88th
Verdichtergehäusecompressor housing
99
Strömungskanalflow channel
1010
Spiralgehäusevolute
1111
Umgelenkter KanalabschnittDeflected channel section
1212
GehäuseeinsatzstückHousing insert
1313
Innenkontur von 12Inner contour of 12
1414
Axialer KanalabschnittAxial duct section
1515
Innenzylinderinner cylinder
1616
Hohlraumcavity
1717
Flexible FixierungFlexible fixation
1818
Starre FixierungRigid fixation
1919
Wand von 1Wall of 1
2020
Spitze von 6Top of 6
2121
Spaltgap
2222
Trennfuge zwischen Spiral- und LagergehäuseParting line between spiral and bearing housing
2323
FlächenmittelpunktCentroid
2424
Grösster Querschnitt des umgelnkten KanalabschnittsLargest cross-section of the looped channel section
AA
axiale Richtungaxial direction
BB
radiale Richtungradial direction

Claims (5)

  1. A centrifugal compressor having a compressor impeller (3) which is received on a shaft (2) mounted in a bearing housing (1) of the centrifugal compressor and which is arranged in a compressor housing (8), wherein the outer contour (6) of the hub (4) of the compressor impeller (3) and the inner contour (7) of the compressor housing (8) form a flow channel (9) which is deflected from the axial direction into the radial direction, and the compressor housing (8) is fixed by means of a rigid fastening (18) on the bearing housing (1), wherein the compressor housing (8) is built out of an outer spiral housing (10), which embraces the channel section (11) of the flow channel (9) that is outwardly deflected in the radial direction (B), and an inner housing insert piece (12) that is between the spiral housing (10) and the compressor impeller (3) and whose inner contour (13) with the outer contour (6) of the hub (4) of the compressor impeller (3) forms the channel section (14) of the flow channel (9) that substantially extends in the axial direction (A), characterised in that the spiral housing (10) is realized with an inner cylinder (15) that at least partially surrounds the housing insert piece (12) and to this cylinder the housing insert piece (12) is attached, so as to form a hollow space (16), by means of a fastening (17) which is flexible in the axial direction (A) and which is realized by means of an expansion-screw fastening in the axial direction (A) through the inner cylinder (15) of the spiral housing (10) in order to be less resistant to breaking than the rigid fastening (18) of the compressor housing (8) on the bearing housing (1).
  2. A centrifugal compressor according to claim 1, characterised in that the rigid fastening (18) of the compressor housing (8) is realized by means of a firm flanged connection of the spiral housing (10) on the bearing housing (1).
  3. A centrifugal compressor according to claim 1, characterised in that the wall (19) of the bearing housing (1) that is provided for the rigid fastening (18) of the spiral housing (10) is arranged so that it is drawn down in the radial direction (B) until it is over the outer tip (20) of the outer contour (6) of the hub (4) of the compressor impeller (3) with the formation of a gap (21).
  4. A centrifugal compressor according to one of the preceding claims, characterised in that the compressor housing (8) is set on the bearing housing (1) by way of the outer spiral housing (10), with the formation of a separating line (22), in such a way that the outer spiral housing (10), which contains the deflected channel section (11), is extended inwards past the rigid fastening (18) in the radial direction B so that the rigid fastening (18) is arranged to lie further outwardly in the radial direction B than the separating line (22) between the spiral housing 10 and the bearing housing 1.
  5. A centrifugal compressor according to claim 5, characterised in that the distance between the separating line (22) and the shaft (2) is smaller than the distance of the area centre (23) of the greatest cross-sectional area (24) through the deflected channel section (11) in the spiral housing (10) to the shaft (2).
EP02003087A 2001-02-20 2002-02-13 Centrifugal compressor Expired - Lifetime EP1233190B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10107807 2001-02-20
DE10107807A DE10107807C1 (en) 2001-02-20 2001-02-20 Flow machine with radial compressor wheel, used as a turbosupercharger, has cavity between inner cylinder of spiral casing and casing insertion piece

Publications (2)

Publication Number Publication Date
EP1233190A1 EP1233190A1 (en) 2002-08-21
EP1233190B1 true EP1233190B1 (en) 2010-06-02

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Application Number Title Priority Date Filing Date
EP02003087A Expired - Lifetime EP1233190B1 (en) 2001-02-20 2002-02-13 Centrifugal compressor

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US (1) US6638007B2 (en)
EP (1) EP1233190B1 (en)
JP (1) JP4119654B2 (en)
KR (1) KR100794974B1 (en)
CN (1) CN1267648C (en)
DE (2) DE10107807C1 (en)

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Also Published As

Publication number Publication date
DE10107807C1 (en) 2002-07-25
KR100794974B1 (en) 2008-01-15
EP1233190A1 (en) 2002-08-21
US6638007B2 (en) 2003-10-28
JP2002257092A (en) 2002-09-11
CN1372082A (en) 2002-10-02
US20020114693A1 (en) 2002-08-22
KR20020068271A (en) 2002-08-27
DE50214459D1 (en) 2010-07-15
CN1267648C (en) 2006-08-02
JP4119654B2 (en) 2008-07-16

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