EP1233190A1 - Turbomachine with radial-flow compressor impeller - Google Patents
Turbomachine with radial-flow compressor impeller Download PDFInfo
- Publication number
- EP1233190A1 EP1233190A1 EP02003087A EP02003087A EP1233190A1 EP 1233190 A1 EP1233190 A1 EP 1233190A1 EP 02003087 A EP02003087 A EP 02003087A EP 02003087 A EP02003087 A EP 02003087A EP 1233190 A1 EP1233190 A1 EP 1233190A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- compressor
- spiral
- fixation
- insert
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
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 turbomachine with radial flow Compressor wheel, which consists of a spiral compressor housing with a helical flow channel is enclosed, according to the preamble of claim 1.
- Such compressor housings are usually used by turbochargers and their Built-in fixtures.
- Smaller turbochargers can be stiff due to the relatively large wall thicknesses Housing parts absorb these forces. With large turbochargers, the Housing wall thicknesses mostly reduced for reasons of casting technology, whereby with such stress the breaking point of the material is quickly reached and housing breakages can occur. Fragments from the Turbocharger leak, with considerable consequential damage.
- the compressor housing is an outer volute casing, which the in the radial direction outwardly deflected channel section of the flow channel comprises, and an inner housing insert which in the radial direction between the volute and the compressor wheel is provided and its Inner contour with the outer contour of the hub of the compressor wheel substantially in the axial direction channel section of the Forms flow channel, has the volute with a Housing insert piece at least partially executed inner cylinder is on this the housing insert to form a cavity by means of a flexible fixation is attached in the axial direction, and the flexible fixation of the housing insert less shatterproof than the rigid fixation of the Compressor housing on the bearing housing is a spiral housing with a "crumple zone", from which no fragment of a burst impeller can leak more.
- the kinetic energy of Fragments of a bursting compressor wheel can now be inside the Turbocharger can be completely converted into deformation energy and heat.
- volute casing intended wall of the bearing housing in the radial direction up to the outer Tip of the outer contour of the compressor wheel, forming a gap arranged pulled down, so that an additional "brake”, that is Protection against radial leakage of fragments of the compressor wheel is specified.
- Parting line on the bearing housing is that the outer, the deflected Spiral housing comprising channel section on the rigid fixation of the Compressor housing past the bearing housing in the radial direction B inwards is pulled, so that the rigid fixation in the radial direction B further out lying as the parting line between the spiral and bearing housing is arranged.
- This measure of the special arrangement of the parting line ensures that the rigid fixation of the compressor housing on the bearing housing from possibly yourself fragments wedging in the flow channel is hardly loaded, thereby causing a Breakage of the compressor housing is further excluded.
- the exhaust gas turbocharger of the type on which the drawing is based has an in their central longitudinal region in a bearing housing 1 shaft 2, which their ends projecting over the bearing are not shown here Turbine wheel and a radial shown schematically in the drawing flows through the compressor wheel 3 carries.
- the compressor wheel 3 shown has one on the through the turbine wheel driven shaft 2 rotatably received hub 4, the circumferential side is occupied with radially projecting blades 5.
- the outer contour 6 of the hub 4 limits with the inner contour 7 of a compressor housing 8 one of the axial Directed in direction A in the radial direction B, narrowing outwards Flow channel 9, the cross section of the configuration of the blades 5 equivalent.
- the compressor housing 8 is by means of a rigid fixation 18 Bearing housing 1 attached.
- the diameter of the hub 4 and the blades 5 increases from the flow inlet to the flow outlet, so that one to Central transverse plane of the compressor wheel 3 asymmetrical longitudinal cross section and accordingly also increasing over the length of the compressor wheel 3 Mass distribution result.
- the compressor housing 8 is from an outer on the bearing housing by means of the rigid fixation 18 moored spiral housing 10, which in the radial Direction B outwardly deflected channel section 11 of the flow channel 9 comprises, and an inner housing insert 12 which in the radial direction B is provided between the volute casing 10 and the compressor wheel 3 and whose inner contour 13 with the outer contour 6 of the hub 4 of the compressor wheel 3 which extends essentially in the axial direction A channel section 14 of the Forms flow channel 9, built.
- the compressor housing 8 is under the outer spiral housing 10
- Forming a parting line 22 on the bearing housing 1 is that the outer spiral housing 10 comprising the deflected channel section 11 the rigid fixation 18 of the compressor housing 8 past the bearing housing 1 in radial direction B is pulled inwards so that the rigid fixation 18 in radial direction B lying further outwards than the parting line 22 between spiral 10 and bearing housing 1 is arranged.
- This measure the special Arrangement of the parting line 22 ensures that the rigid fixation 18 of the Compressor housing 8 on the bearing housing 1 of possibly in the flow channel 9 wedging fragments is hardly loaded, causing the Compressor housing 8 is excluded even further.
- the distance between the Parting line 22 and the shaft 2 smaller than the distance from the center of the surface 23 of the largest cross-sectional area 24 through the deflected channel section 11 in the spiral housing 10 to the shaft 2.
- the spiral housing 10 is at least with the housing insert 12 partially surrounding inner cylinder 15 executed on this Housing insert 12 for forming a cavity 16 by means of a axial direction A flexible fixation 17 is attached.
- the flexible fixation 17 the housing insert 12 is significantly less shatterproof than the rigid fixation 18 of the spiral housing 10 on the bearing housing 1.
- the rigid fixation 18 of the compressor housing 8 or the spiral housing 10 is by means of a fixed flange connection of the spiral housing 10 on the bearing housing 1 and the flexible fixation 17 of the housing insert 12 by means of a Expansion screw fixation in the axial direction A through the inner cylinder 15 of the Spiral casing 10 executed.
- the provided for rigid fixation 18 of the volute 8 wall 19 of the Bearing housing 1 is in the radial direction B to over the outer tip 20 of the Outer contour 6 of the hub 4 of the compressor wheel 3, forming a gap 21 arranged pulled down.
- the spiral housing 10 is always inward in the direction of the compressor wheel 3 decreasing diameter of the flow channel 9 executed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Supercharger (AREA)
Abstract
Um eine Strömungsmaschine mit radial durchströmten Verdichterrad (3) und einem Verdichtergehäuse (8) mit einem schneckenförmigen Strömungskanal (9), das mittels einer starren Fixierung (18) am Lagergehäuse (1) der Strömungsmaschine festgelegt ist, mit einfachen und kostengünstigen Mitteln so weiterzubilden, dass das Austreten von Bruchstücken eines geborstenen Verdichterrades aus dem Verdichtergehäuse verhindert werden kann, ist vorgesehen, dass das Verdichtergehäuse (8) ein äusseres Spiralgehäuse (10), das den in die radiale Richtung (B) nach aussen umgelenkten Kanalabschnitt (11) des Strömungskanals (9) umfasst, und ein inneres 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, aufweist, dass das Spiralgehäuse (10) mit einem das Gehäuseeinsatzstück (12) zumindest teilweise umgebenden Innenzylinder (15) ausgeführt ist, an diesem das Gehäuseeinsatzstück (12) zur Ausbildung eines Hohlraumes (16) mittels einer in axialer Richtung (A) flexiblen Fixierung (17) angebaut ist, und die flexible Fixierung (17) des Gehäuseeinsatzes (12) weniger bruchsicher als die starre Fixierung (18) des Verdichtergehäuses (8) am Lagergehäuse (1) ausgeführt ist. <IMAGE>In order to further develop a turbomachine with a compressor wheel (3) with a radial flow and a compressor housing (8) with a helical flow channel (9), which is fixed to the bearing housing (1) of the turbomachine by means of a rigid fixation (18), using simple and inexpensive means, In order to prevent fragments of a burst compressor wheel from escaping from the compressor housing, it is provided that the compressor housing (8) has an outer spiral housing (10), which surrounds the channel section (11) of the flow channel (11) deflected outward in the radial direction (B). 9), and an inner housing insert (12), which is provided in the radial direction (B) between the spiral housing (10) and the compressor wheel (3) and whose inner contour (13) with the outer contour (6) of the hub (4) of the compressor wheel (3) forms the channel section (14) of the flow channel (9) running essentially in the axial direction (A), that the spiral housing (10) is designed with an inner cylinder (15) at least partially surrounding the housing insert (12), on which the housing insert (12) is attached to form a cavity (16) by means of a fixing (17) that is flexible in the axial direction (A) and the flexible fixation (17) of the housing insert (12) is less break-proof than the rigid fixation (18) of the compressor housing (8) on the bearing housing (1). <IMAGE>
Description
Die Erfindung betrifft eine Strömungsmaschine mit radial durchströmten
Verdichterrad, das von einem spiralförmigen Verdichtergehäuse mit einem
schneckenförmigen Strömungskanal umschlossen ist, gemäß dem Oberbegriff
des Patentanspruchs 1.The invention relates to a turbomachine with radial flow
Compressor wheel, which consists of a spiral compressor housing with a
helical flow channel is enclosed, according to the preamble
of
Der grundsätzliche Aufbau und die Wirkungsweise derartiger Strömungsmaschinen, wie z. B. ein Radialverdichter 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 eine gattungsbildende Strömungsmaschine in Form eines Radialverdichters 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 mode of operation of such Fluid machines, such as B. a radial compressor of a turbocharger are on are known and therefore do not need any further details in the present context Explanation more. For example, in DE 195 02 808 C2 Generic fluid flow machine in the form of a radial compressor Turbocharger described, within the spiral compressor housing the Diameter of the hub of the compressor wheel and the blades in Direction of flow increases and the outer contour of the blades is curved ' and the inner contour of the neighboring, toroidally curved outwards Corresponds to the channel wall of the helical flow channel, the Duct wall of the compressor housing with the outer contour of the hub of the Limit a duct section deflected outwards, in these engage the blades. On these radially deflected outwards Channel section closes an annular that opens into a spiral channel Channel section.
Üblicherweise werden derartige Verdichtergehäuse von Turboladern und deren Einbauten starr ausgeführt.Such compressor housings are usually used by turbochargers and their Built-in fixtures.
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, this can occur Compressor wheel are weakened so much by corrosion, erosion and aging, that the bursting of the compressor wheel cannot be excluded. in the In the event of a compressor wheel break, in which the wheel mostly in two or three If large sections are broken, these individual parts are damaged by the considerable Centrifugal forces thrown outwards. It can even be broken emerge from the compressor housing. In doing so, the compressor wheel blades completely destroyed and the remaining hub body jams between the Bearing housing and the compressor housing. By shaping the Hub pieces create a wedge effect that is considerable impulsive Apply axial forces to 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 be stiff due to the relatively large wall thicknesses Housing parts absorb these forces. With large turbochargers, the Housing wall thicknesses mostly reduced for reasons of casting technology, whereby with such stress the breaking point of the material is quickly reached and housing breakages can occur. Fragments from the Turbocharger leak, 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 definitely be avoided. For this purpose, it is common today outside the compressor housing receiving the compressor wheel provide additional burst protection.
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.Proceeding from this, it is therefore the object of the present invention to provide a Turbomachine of the type mentioned at the beginning with simple and inexpensive Means to develop so that the leakage of fragments of a burst compressor wheel can be prevented from the compressor housing can, without an additional burst protection outside the volute. to have to provide.
Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des
Patentanspruchs 1 gelöst. This object is achieved by the characterizing features of
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.The fact that the compressor housing is an outer volute casing, which the in the radial direction outwardly deflected channel section of the flow channel comprises, and an inner housing insert which in the radial direction between the volute and the compressor wheel is provided and its Inner contour with the outer contour of the hub of the compressor wheel substantially in the axial direction channel section of the Forms flow channel, has the volute with a Housing insert piece at least partially executed inner cylinder is on this the housing insert to form a cavity by means of a flexible fixation is attached in the axial direction, and the flexible fixation of the housing insert less shatterproof than the rigid fixation of the Compressor housing on the bearing housing is a spiral housing with a "crumple zone", from which no fragment of a burst impeller can leak more. The kinetic energy of Fragments of a bursting compressor wheel can now be inside the Turbocharger can be completely converted into deformation energy and heat.
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 fixing of the volute on the bearing housing, as well the housing insert itself has significantly more kinetic energy than the flexible one Fixation of the housing insert on the volute casing can take ensures that the housing insert is in the axial direction in an emergency can move away from the compressor wheel. So the kinetic energy of the Compressor wheel pieces by conversion into deformation energy and from it resulting heat are largely absorbed. The remaining one kinetic energy of the fragments can be absorbed by the casings become.
Ein zusätzlicher Berstschutz ausserhalb des Spiralgehäuses kann entfallen. Additional burst protection outside the volute casing 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. In besonders vorteilhafter Weise 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.The fact that the spiral housing with the housing insert at least partially surrounding inner cylinder is executed on this Housing insert for forming a cavity by means of an axial Attached to flexible fixation is a high protection against smashing of the volute casing itself and an effective "brake" against one Escaping fragments given the turbocharger. Especially The rigid fixation of the compressor housing by means of a fixed flange connection of the volute on the bearing housing and the flexible Fixing the housing insert by means of an expansion screw fixation in axial direction through the inner cylinder of the volute.
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.It is particularly advantageous for rigidly fixing the volute casing intended wall of the bearing housing in the radial direction up to the outer Tip of the outer contour of the compressor wheel, forming a gap arranged pulled down, so that an additional "brake", that is Protection against radial leakage 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 ausen 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. Another particularly advantageous training is the fact that Compressor housing over the outer volute casing in such a way Parting line on the bearing housing is that the outer, the deflected Spiral housing comprising channel section on the rigid fixation of the Compressor housing past the bearing housing in the radial direction B inwards is pulled, so that the rigid fixation in the radial direction B further out lying as the parting line between the spiral and bearing housing is arranged. This measure of the special arrangement of the parting line ensures that the rigid fixation of the compressor housing on the bearing housing from possibly yourself fragments wedging in the flow channel is hardly loaded, thereby causing a Breakage of the compressor housing is further excluded.
Die Erfindung soll nachfolgend aus einer Beispielsbeschreibung anhand der Zeichnung näher erläutert werden.The invention will follow from an example description based on the Drawing will be explained in more detail.
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 a Turbomachine according to the invention in the form of a radial 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 on which the drawing is based has an in
their central longitudinal region in a bearing
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 compressor wheel 3 shown has one on the through the turbine wheel
driven shaft 2 rotatably received
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
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
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.In the exemplary embodiment, the distance between the
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
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
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 provided for
Das Spiralgehäuse 10 ist mit nach innen in Richtung des Verdichterrades 3 immer
kleiner werdenden Durchmesser des Strömungskanals 9 ausgeführt. The
- 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 KanalabschnittRedirected channel section
- 1212
- GehäuseeinsatzstückHousing insert
- 1313
- Innenkontur von 12Inner contour of 12
- 1414
- Axialer KanalabschnittAxial channel 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 LagergehäusePartition between spiral and bearing housing
- 2323
- FlächenmittelpunktCentroid
- 2424
- Grösster Querschnitt des umgelnkten KanalabschnittsLargest cross section of the redirected channel section
- AA
- axiale Richtungaxial direction
- BB
- radiale Richtungradial direction
Claims (6)
dadurch gekennzeichnet, dass das Verdichtergehäuse (8) aus einem äusseren Spiralgehäuse (10), das den in die radiale Richtung (B) nach aussen umgelenkten Kanalabschnitt (11) des Strömungskanals (9) umfasst, und einem inneren Gehäuseeinsatzstück (12) zwischen dem Spiralgehäuse (10) und dem Verdichterrad (3), 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, gebaut ist, das Spiralgehäuse (10) mit einem das Gehäuseeinsatzstück (12) zumindest teilweise umgebenden Innenzylinder (15) ausgeführt ist, an diesem das Gehäuseeinsatzstück (12) zur Ausbildung eines Hohlraumes (16) mittels einer in axialer Richtung (A) flexiblen Fixierung (17) angebaut ist, und die flexible Fixierung (17) des Gehäuseeinsatzes (12) weniger bruchsicher als die starre Fixierung (18) des Verdichtergehäuses (8) am Lagergehäuse (1) ausgeführt ist. Turbomachine with a radially flowing compressor wheel (3), which is received on a shaft (2) mounted in a bearing housing (1) of the turbomachine and is arranged in a compressor housing (8) with a helical flow channel (9), the outer contour (6) of the The hub (4) of the compressor wheel (3) and the inner contour (7) of the compressor housing (8) form a flow channel (9) deflected from the axial into the radial direction, and the compressor housing (8) is attached to the bearing housing (8) by means of a rigid fixation (18). 1) is determined
characterized in that the compressor housing (8) comprises an outer spiral housing (10), which comprises the channel section (11) of the flow channel (9) deflected outward in the radial direction (B), and an inner housing insert (12) between the spiral housing (10) and the compressor wheel (3), the inner contour (13) of which, with the outer contour (6) of the hub (4) of the compressor wheel (3), the channel section (14) of the flow channel (9) which extends essentially in the axial direction (A). forms, is built, the spiral housing (10) is designed with an inner cylinder (15) at least partially surrounding the housing insert (12), on this the housing insert (12) to form a cavity (16) by means of a flexible in the axial direction (A) Fixation (17) is attached, and the flexible fixation (17) of the housing insert (12) is less breakproof than the rigid fixation (18) of the compressor housing (8) on the bearing housing (1).
dadurch gekennzeichnet, dass die starre Fixierung (18) des Verdichtergehäuses (8) mittels einer festen Flanschverbindung des Spiralgehäuses (10) am Lagergehäuse (1) ausgeführt ist.Fluid machine according to claim 1,
characterized in that the rigid fixation (18) of the compressor housing (8) is carried out by means of a fixed flange connection of the volute housing (10) on the bearing housing (1).
dadurch gekennzeichnet, dass die flexible Fixierung (17) des Gehäuseeinsatzstückes (10) mittels einer Dehnschraubenfixierung in axialer Richtung (A) durch den Innenzylinder (15) des Spiralgehäuses (10) ausgeführt ist.Fluid machine according to claim 1,
characterized in that the flexible fixation (17) of the housing insert (10) is carried out by means of an expansion screw fixation in the axial direction (A) through the inner cylinder (15) of the volute casing (10).
dadurch gekennzeichnet, dass die zur starren Fixierung (18) des Spiralgehäuses (10) vorgesehene Wand (19) des Lagergehäuses (1) 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 ist. Fluid machine according to claim 1,
characterized in that the wall (19) of the bearing housing (1) provided for rigid fixation (18) of the spiral housing (10) in the radial direction (B) to beyond the outer tip (20) of the outer contour (6) of the hub (4) the compressor wheel (3) is arranged pulled down to form a gap (21).
dadurch gekennzeichnet, dass das Verdichtergehäuse (8) 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) 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.Fluid machine according to one of the preceding claims,
characterized in that the compressor housing (8) is attached to the bearing housing (1) via the outer spiral housing (10), forming a parting line (22),
that the outer spiral housing (10) comprising the deflected channel section (11) is pulled past the rigid fixation (18) in the radial direction B, so that the rigid fixation (18) lies further out in the radial direction B than the parting line (22) between the spiral 10 and bearing housing 1 is arranged.
dadurch gekennzeichnet, dass 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) ist.Fluid machine according to claim 5,
characterized in that the distance between the parting line (22) and the shaft (2) is smaller than the distance from the center of the surface (23) of the largest cross-sectional area (24) through the deflected channel section (11) in the spiral housing (10) to the shaft (2) is.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| 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 |
| DE10107807 | 2001-02-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1233190A1 true EP1233190A1 (en) | 2002-08-21 |
| EP1233190B1 EP1233190B1 (en) | 2010-06-02 |
Family
ID=7674629
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02003087A Expired - Lifetime EP1233190B1 (en) | 2001-02-20 | 2002-02-13 | Centrifugal compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US6638007B2 (en) |
| EP (1) | EP1233190B1 (en) |
| JP (1) | JP4119654B2 (en) |
| KR (1) | KR100794974B1 (en) |
| CN (1) | CN1267648C (en) |
| DE (2) | DE10107807C1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2414769A (en) * | 2004-06-05 | 2005-12-07 | Man B & W Diesel Ag | Turbo-machine with impeller containment assembly. |
| DE102004028133A1 (en) | 2004-06-09 | 2006-01-05 | Man B & W Diesel Ag | Turbo-machine e.g. turbocharger, has flexible fixation provided with fitting bolt that comprises waisted shank and fitting pin, where pin is guided in flange part and/or hole of insert piece and spiral casing for receiving force |
| DE102004044703A1 (en) * | 2004-09-15 | 2006-03-16 | Volkswagen Ag | Exhaust gas turbocharger for internal combustion engine, has anti-fatigue bolt provided in bearing housing for fastening guide vane carrier and flow channel unit and gripping through unit and carrier |
| DE102005039820A1 (en) * | 2005-08-22 | 2007-03-01 | Man Diesel Se | Dynamic type compressor e.g. radial compressor of turbocharger, has ring-shaped bar, which locks inner housing insert into outer spiral housing using compressive force acting on outer spiral housing, during bursting of compressor wheel |
| DE102008056512A1 (en) | 2008-11-08 | 2010-05-12 | Man Diesel Se | Compressor housing for fluid-flow machine, has spiral shaped flow channel, where its cross section increases continuously to discharge part of compressor housing |
| US8932008B2 (en) | 2008-04-08 | 2015-01-13 | Continental Automotive Gmbh | Securing element and exhaust gas turbocharger having variable turbine geometry |
| DE102018102704A1 (en) * | 2018-02-07 | 2019-08-08 | Man Energy Solutions Se | centrifugal compressors |
Families Citing this family (42)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1586745B1 (en) * | 2004-04-13 | 2015-07-29 | ABB Turbo Systems AG | Compressor casing |
| US20060127242A1 (en) * | 2004-12-09 | 2006-06-15 | Martin Steve P | Turbocharger with removable wheel shrouds and/or removable seals |
| DE102005025865A1 (en) * | 2005-06-06 | 2006-12-07 | Gebr. Becker Gmbh & Co Kg | Radial fan e.g. for high-speed radial fan, has blower wheel, housing which receives rotor and stator of electrical drive of blower wheel shaft and cooling system |
| CN101793257B (en) * | 2005-06-06 | 2013-06-19 | 格布尔·贝克尔有限责任公司 | Radial fan |
| US7568338B2 (en) * | 2005-12-23 | 2009-08-04 | Honeywell International Inc. | Multi-piece compressor housing |
| US8108003B2 (en) * | 2006-03-09 | 2012-01-31 | Alcatel Lucent | Controlling base station router device definition codes |
| US7874136B2 (en) * | 2006-04-27 | 2011-01-25 | Pratt & Whitney Canada Corp. | Rotor containment element with frangible connections |
| WO2008055717A1 (en) | 2006-11-10 | 2008-05-15 | Abb Turbo Systems Ag | Housing connection of an exhaust gas turbocharger |
| CN100451345C (en) * | 2007-02-02 | 2009-01-14 | 清华大学 | Centrifugal compressor having air removal jet box structure |
| CN101965460B (en) * | 2007-11-20 | 2014-08-13 | 曼·胡默尔有限公司 | Housing for a radial compressor |
| DE102007055615A1 (en) * | 2007-11-20 | 2009-05-28 | Mann + Hummel Gmbh | Housing for a centrifugal compressor |
| DE102008025249A1 (en) * | 2008-05-27 | 2009-12-03 | Siemens Aktiengesellschaft | Collecting room and process for production |
| US8235648B2 (en) | 2008-09-26 | 2012-08-07 | Pratt & Whitney Canada Corp. | Diffuser with enhanced surge margin |
| DE102008061398A1 (en) | 2008-12-10 | 2010-06-17 | Man Diesel Se | Method for creating burst protection for flow machine, particularly exhaust gas turbocharger, involves wrapping machine housing of flow machine partially with metal or Kevlar netting |
| GB0912796D0 (en) | 2009-07-23 | 2009-08-26 | Cummins Turbo Tech Ltd | Compressor,turbine and turbocharger |
| US8984895B2 (en) * | 2010-07-09 | 2015-03-24 | Icr Turbine Engine Corporation | Metallic ceramic spool for a gas turbine engine |
| US9051873B2 (en) | 2011-05-20 | 2015-06-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine shaft attachment |
| US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
| DE102012217381A1 (en) * | 2012-09-26 | 2014-03-27 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Radial compressor for an exhaust gas turbocharger |
| GB2517482B (en) * | 2013-08-22 | 2020-02-26 | Napier Turbochargers Ltd | Turbocharger |
| ITCO20130067A1 (en) * | 2013-12-17 | 2015-06-18 | Nuovo Pignone Srl | IMPELLER WITH PROTECTION ELEMENTS AND CENTRIFUGAL COMPRESSOR |
| JP6133439B2 (en) * | 2013-12-24 | 2017-05-24 | 三菱重工業株式会社 | Compressor and turbocharger |
| JP6234480B2 (en) * | 2013-12-27 | 2017-11-22 | 三菱重工業株式会社 | compressor |
| JP6391970B2 (en) * | 2014-03-31 | 2018-09-19 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, centrifugal compressor manufacturing method, and silencer |
| DE102014106415A1 (en) * | 2014-05-08 | 2015-11-12 | Abb Turbo Systems Ag | compressor housing |
| JP6486648B2 (en) * | 2014-10-28 | 2019-03-20 | 三菱重工業株式会社 | Centrifugal compressor and supercharger provided with the same |
| US9995179B2 (en) | 2014-12-17 | 2018-06-12 | Progress Rail Locomotive Inc. | Compressor assembly for turbocharger burst containment |
| DE102015005054A1 (en) * | 2015-04-21 | 2016-10-27 | Man Diesel & Turbo Se | flow machine |
| US10526954B2 (en) | 2015-08-06 | 2020-01-07 | Garrett Transportation I Inc. | Turbocharger assembly |
| CN105065328B (en) * | 2015-08-06 | 2017-11-14 | 中国北方发动机研究所(天津) | A kind of double flute for centrifugal compressor automatically adjusts casing processing unit |
| US9926942B2 (en) | 2015-10-27 | 2018-03-27 | Pratt & Whitney Canada Corp. | Diffuser pipe with vortex generators |
| US10570925B2 (en) | 2015-10-27 | 2020-02-25 | Pratt & Whitney Canada Corp. | Diffuser pipe with splitter vane |
| CN108474390B (en) * | 2016-02-15 | 2020-11-10 | 三菱重工发动机和增压器株式会社 | Centrifugal compressor and supercharger |
| CN106121748B (en) * | 2016-08-30 | 2017-09-29 | 湖南天雁机械有限责任公司 | Turbocharger pressure shell with air inlet and gas outlet connector |
| US10823197B2 (en) | 2016-12-20 | 2020-11-03 | Pratt & Whitney Canada Corp. | Vane diffuser and method for controlling a compressor having same |
| US10494955B2 (en) * | 2017-01-30 | 2019-12-03 | Garrett Transportation I Inc. | Sheet metal turbine housing with containment dampers |
| WO2019060754A2 (en) * | 2017-09-25 | 2019-03-28 | Johnson Controls Technology Company | Two piece split scroll for centrifugal compressor |
| DE102017221717A1 (en) * | 2017-12-01 | 2019-06-06 | Man Energy Solutions Se | centrifugal compressors |
| DE102018110235A1 (en) * | 2018-04-27 | 2019-10-31 | Man Energy Solutions Se | turbocharger |
| US11187149B2 (en) * | 2019-11-25 | 2021-11-30 | Transportation Ip Holdings, Llc | Case-integrated turbomachine wheel containment |
| JP7562357B2 (en) * | 2020-09-30 | 2024-10-07 | 三菱重工マリンマシナリ株式会社 | Rotating Machinery |
| US11614001B1 (en) * | 2021-11-11 | 2023-03-28 | Progress Rail Locomotive Inc. | Turbine containment |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4223496A1 (en) * | 1992-07-17 | 1994-01-20 | Asea Brown Boveri | Reducing kinetic energy of bursting parts in turbines - involves crumple zone between inner and outer rings set between housing and rotor to absorb energy and contain fractured parts |
| DE19502808A1 (en) * | 1995-01-30 | 1996-08-08 | Man B & W Diesel Ag | Radial-flow compressor with deflected flow duct |
| EP0834646A1 (en) * | 1996-10-02 | 1998-04-08 | Asea Brown Boveri AG | Containment device for the radial turbine of a turbocharger |
| DE19727139A1 (en) * | 1997-06-26 | 1999-01-07 | Daimler Benz Ag | Compressor for exhaust gas turbocharger |
| US5934868A (en) * | 1996-05-08 | 1999-08-10 | Asea Brown Boveri Ag | Axial turbine of an exhaust-gas turbocharger |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3738929A1 (en) * | 1987-11-17 | 1989-05-24 | Leybold Ag | Blower with impeller and guide element |
| US5271220A (en) * | 1992-10-16 | 1993-12-21 | Sundstrand Corporation | Combustor heat shield for a turbine containment ring |
| SE520740C2 (en) * | 1998-06-30 | 2003-08-19 | Abs Pump Prod Ab | centrifugal |
| US6224321B1 (en) * | 1998-12-07 | 2001-05-01 | Pratt & Whitney Canada Inc. | Impeller containment system |
-
2001
- 2001-02-20 DE DE10107807A patent/DE10107807C1/en not_active Expired - Fee Related
-
2002
- 2002-02-06 US US10/072,585 patent/US6638007B2/en not_active Expired - Fee Related
- 2002-02-13 DE DE50214459T patent/DE50214459D1/en not_active Expired - Lifetime
- 2002-02-13 EP EP02003087A patent/EP1233190B1/en not_active Expired - Lifetime
- 2002-02-15 JP JP2002037633A patent/JP4119654B2/en not_active Expired - Fee Related
- 2002-02-18 KR KR1020020008406A patent/KR100794974B1/en active IP Right Grant
- 2002-02-20 CN CNB021046859A patent/CN1267648C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4223496A1 (en) * | 1992-07-17 | 1994-01-20 | Asea Brown Boveri | Reducing kinetic energy of bursting parts in turbines - involves crumple zone between inner and outer rings set between housing and rotor to absorb energy and contain fractured parts |
| DE19502808A1 (en) * | 1995-01-30 | 1996-08-08 | Man B & W Diesel Ag | Radial-flow compressor with deflected flow duct |
| US5934868A (en) * | 1996-05-08 | 1999-08-10 | Asea Brown Boveri Ag | Axial turbine of an exhaust-gas turbocharger |
| EP0834646A1 (en) * | 1996-10-02 | 1998-04-08 | Asea Brown Boveri AG | Containment device for the radial turbine of a turbocharger |
| DE19727139A1 (en) * | 1997-06-26 | 1999-01-07 | Daimler Benz Ag | Compressor for exhaust gas turbocharger |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1707123B (en) * | 2004-06-05 | 2010-08-18 | 曼·B及W柴油机公开股份有限公司 | Turbo-machine with radial through-flow compressor rotor |
| FR2871201A1 (en) * | 2004-06-05 | 2005-12-09 | Man B & W Diesel Ag | FLUIDIC MACHINE WITH RADIAL COMPRESSOR ROTOR |
| DE102004027594A1 (en) * | 2004-06-05 | 2005-12-29 | Man B & W Diesel Ag | Turbomachine with radially flowing compressor wheel |
| DE102004027594B4 (en) * | 2004-06-05 | 2006-06-29 | Man B & W Diesel Ag | Turbomachine with radially flowing compressor wheel |
| GB2414769A (en) * | 2004-06-05 | 2005-12-07 | Man B & W Diesel Ag | Turbo-machine with impeller containment assembly. |
| GB2414769B (en) * | 2004-06-05 | 2009-11-04 | Man B & W Diesel Ag | Turbo-machine having a compressor wheel with radial flow |
| DE102004028133A1 (en) | 2004-06-09 | 2006-01-05 | Man B & W Diesel Ag | Turbo-machine e.g. turbocharger, has flexible fixation provided with fitting bolt that comprises waisted shank and fitting pin, where pin is guided in flange part and/or hole of insert piece and spiral casing for receiving force |
| DE102004028133B4 (en) | 2004-06-09 | 2006-06-01 | Man B & W Diesel Ag | Turbomachine, in particular exhaust gas turbocharger |
| DE102004028133C5 (en) * | 2004-06-09 | 2017-10-26 | Man Diesel & Turbo Se | Turbomachine, in particular exhaust gas turbocharger |
| DE102004044703A1 (en) * | 2004-09-15 | 2006-03-16 | Volkswagen Ag | Exhaust gas turbocharger for internal combustion engine, has anti-fatigue bolt provided in bearing housing for fastening guide vane carrier and flow channel unit and gripping through unit and carrier |
| DE102005039820B4 (en) * | 2005-08-22 | 2007-06-28 | Man Diesel Se | Containment safety device for turbomachinery with radial flow compressor wheel |
| DE102005039820A1 (en) * | 2005-08-22 | 2007-03-01 | Man Diesel Se | Dynamic type compressor e.g. radial compressor of turbocharger, has ring-shaped bar, which locks inner housing insert into outer spiral housing using compressive force acting on outer spiral housing, during bursting of compressor wheel |
| US8932008B2 (en) | 2008-04-08 | 2015-01-13 | Continental Automotive Gmbh | Securing element and exhaust gas turbocharger having variable turbine geometry |
| DE102008056512A1 (en) | 2008-11-08 | 2010-05-12 | Man Diesel Se | Compressor housing for fluid-flow machine, has spiral shaped flow channel, where its cross section increases continuously to discharge part of compressor housing |
| DE102008056512B4 (en) * | 2008-11-08 | 2016-07-21 | Man Diesel & Turbo Se | Compressor housing of a turbomachine with helical flow channel |
| DE102018102704A1 (en) * | 2018-02-07 | 2019-08-08 | Man Energy Solutions Se | centrifugal compressors |
Also Published As
| Publication number | Publication date |
|---|---|
| DE50214459D1 (en) | 2010-07-15 |
| JP4119654B2 (en) | 2008-07-16 |
| US20020114693A1 (en) | 2002-08-22 |
| US6638007B2 (en) | 2003-10-28 |
| CN1267648C (en) | 2006-08-02 |
| DE10107807C1 (en) | 2002-07-25 |
| KR20020068271A (en) | 2002-08-27 |
| CN1372082A (en) | 2002-10-02 |
| EP1233190B1 (en) | 2010-06-02 |
| KR100794974B1 (en) | 2008-01-15 |
| JP2002257092A (en) | 2002-09-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE10107807C1 (en) | Flow machine with radial compressor wheel, used as a turbosupercharger, has cavity between inner cylinder of spiral casing and casing insertion piece | |
| EP1383987B1 (en) | Burst protection device for radial compressors pertaining to turbochargers | |
| EP2216517B1 (en) | Burst protection device for radial compressor | |
| DE3302576C2 (en) | Fan housing with a blade break protection device for an axial gas turbine engine | |
| DE69918162T2 (en) | Rupture protection device for radial turbines | |
| DE102004027594B4 (en) | Turbomachine with radially flowing compressor wheel | |
| CH698497B1 (en) | Turbomachine with radial compressor and perfused with holding device. | |
| EP0834646A1 (en) | Containment device for the radial turbine of a turbocharger | |
| DE19615237A1 (en) | Exhaust gas turbocharger for an internal combustion engine | |
| DE10050931C1 (en) | Turbo machine with impeller with radial flow | |
| CH689400A5 (en) | Centrifugal pump with one-piece diffuser and Abfuehrschaufel channel ring member. | |
| DE102004028133B4 (en) | Turbomachine, in particular exhaust gas turbocharger | |
| DE10125250C5 (en) | Axial turbine of an exhaust turbocharger with internal burst protection | |
| EP0491966A1 (en) | Support device of a thermal turbomachine | |
| DE102008048006B4 (en) | Shaft power engine, in particular for an aircraft, with a cooling gas guide system in the region of the mounting flanges of the rotor disks | |
| DE102008056512B4 (en) | Compressor housing of a turbomachine with helical flow channel | |
| EP1719879A1 (en) | Burst protection device for radial compressors | |
| WO2012110198A1 (en) | Hydraulic turbomachine | |
| EP0267478B1 (en) | Gas turbine jet engine with a high pressure compressor | |
| EP2722485B1 (en) | Inner ring for a stator assembly with adjustable vanes | |
| EP3246521B1 (en) | Discharge area for guide blade cover and base panels | |
| DE102005062562A1 (en) | Automotive turbocharger has a turbine shroud linked via radial links to bearing case | |
| EP1752658B1 (en) | Cross-flow turbine comprising a tangential runner | |
| DE3936262A1 (en) | TURBINE PROTECTION SYSTEM | |
| WO2025016879A1 (en) | Turbo component with energy absorption struts |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
| AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
| 17P | Request for examination filed |
Effective date: 20021107 |
|
| AKX | Designation fees paid |
Designated state(s): CH DE FR GB LI |
|
| 17Q | First examination report despatched |
Effective date: 20080521 |
|
| RTI1 | Title (correction) |
Free format text: CENTRIFUGAL COMPRESSOR |
|
| GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
| RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: SCHMIDT, WOLFGANG Inventor name: BARTHOLOMAE, DR. KLAUS |
|
| RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MAN DIESEL SE |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): CH DE FR GB LI |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: E. BLUM & CO. AG PATENT- UND MARKENANWAELTE VSP Ref country code: CH Ref legal event code: EP |
|
| REF | Corresponds to: |
Ref document number: 50214459 Country of ref document: DE Date of ref document: 20100715 Kind code of ref document: P |
|
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20110303 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 50214459 Country of ref document: DE Effective date: 20110302 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20110213 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20111102 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110228 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110213 |
|
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: PFA Owner name: MAN ENERGY SOLUTIONS SE, DE Free format text: FORMER OWNER: MAN DIESEL AND TURBO SE, DE |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R081 Ref document number: 50214459 Country of ref document: DE Owner name: MAN ENERGY SOLUTIONS SE, DE Free format text: FORMER OWNER: MAN DIESEL & TURBO SE, 86153 AUGSBURG, DE |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20200219 Year of fee payment: 19 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20200219 Year of fee payment: 19 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50214459 Country of ref document: DE |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210228 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210228 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210901 |