EP2452076B1 - Turbomachine impeller - Google Patents

Turbomachine impeller Download PDF

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Publication number
EP2452076B1
EP2452076B1 EP10708100.2A EP10708100A EP2452076B1 EP 2452076 B1 EP2452076 B1 EP 2452076B1 EP 10708100 A EP10708100 A EP 10708100A EP 2452076 B1 EP2452076 B1 EP 2452076B1
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EP
European Patent Office
Prior art keywords
impeller
shrink
collar
circumferential groove
shrink collar
Prior art date
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Not-in-force
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EP10708100.2A
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German (de)
French (fr)
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EP2452076A1 (en
Inventor
Christoph Lange
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MAN Energy Solutions SE
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MAN Diesel and Turbo SE
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Publication date
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Publication of EP2452076A1 publication Critical patent/EP2452076A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/40—Heat treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/37—Retaining components in desired mutual position by a press fit connection
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/4932—Turbomachine making
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/10—Selectively engageable hub to shaft connection

Definitions

  • the invention relates to an impeller for a turbomachine, in particular a radial turbomachine, with an impeller front side and an adjoining shrink collar for shrinking onto a rotor of the turbomachine, and a turbomachine with a rotor and an impeller shrunk thereon.
  • impellers convert energy from a fluid passing through them and mechanical energy from a rotor supporting the impellers.
  • one or more impellers for this purpose are traversed transversely to the axis of rotation of the rotor.
  • Wheels are often by shrink fit seats, i.e. an excess of the rotor outer diameter relative to a wheel inner diameter, axially fixed friction on the rotor.
  • shrink fit seats i.e. an excess of the rotor outer diameter relative to a wheel inner diameter, axially fixed friction on the rotor.
  • known wheels on one or both end faces on shrink collars ie. Axial extensions of the actual impeller disk, which have a smaller diameter.
  • the shrink collars can be additionally secured with Schrumpfbunduxen that pass through aligned holes of the collar and rotor.
  • Such wheels are, for example, from the documents GB 770 004 A . JP S63 26701 U and US 4 697 987 A disclosed.
  • the object of the present invention is to provide an improved turbomachine.
  • Claim 10 presents a turbomachine with such an impeller.
  • the subclaims relate to advantageous developments.
  • An impeller according to the invention is provided for attachment to a rotor of a turbomachine, in particular a radial turbomachine such as a radial compressor or compressor.
  • a shrink collar is provided on at least one impeller end, preferably the downstream back or wall of the rotor blades carrying the rotor blades, which in one preferred embodiment is integral with the impeller disk.
  • a radially outer circumferential groove is formed between the Laufradstimseite and the associated shrinkage collar.
  • a circumferential groove in particular a local reduction in cross section is referred to, as can be prepared for example by piercing the rotating shrink collar with a turning tool.
  • the circumferential groove can be optimized in terms of production, assembly, strength, thermodynamic and / or dynamic aspects.
  • a circumferential groove whose side walls are oriented substantially perpendicular to the axis of rotation of the impeller, particularly simple, for example, cutting, produced.
  • Rounded transitions or edges between groove side walls and groove bottom and / or the radially outer surface of the shrink collar reduce both the risk of injury during assembly and the notch effect with a corresponding impact on the strength, in particular the fatigue strength and susceptibility to vibration.
  • a corresponding dimensioning of groove width and / or depth influences the heat transfer between the impeller disc and shrink collar during operation and during shrinking and the rigidity of the connection of the 1 aufradility to the shrink collar and thus the vibration behavior and expansion of the impeller disc under centrifugal force and axial thrust of the working fluid.
  • the circumferential groove is graduated radially several times, ie in the direction of the axis of rotation of the impeller, it has regions of different outer diameter.
  • the circumferential groove it is also possible for the circumferential groove to have a lateral surface inclined towards the axis of rotation and / or a curved lateral surface.
  • Particularly favorable manufacturing, assembly, and strength engineering, thermodynamic and dynamic properties arise in radial Groove depths in a range between 0.1 times and 0.99 times, in particular 0.3 times and 0.7 times, preferably 0.5 times and 0.65 times, preferably about 0.55 times the radial height of the shrinkage collar. ie the maximum radial distance between inner and outer diameter of the shrinkage collar.
  • the circumferential groove is arranged substantially directly on the impeller front side or the impeller disk so as to achieve a larger contiguous axial seat of the remaining shrink collars.
  • Fig. 1 shows in meridian section a part of a rotor 1 of a radio compressor, on which an impeller 2 is fixed. This has an impeller disc 2.1 and an integral with this Schtumpfbund 2.3, which is disposed on the downstream, facing away from the blades rear 2.2 of the impeller disc 2.1.
  • the impeller 2 has a continuous, cylindrical central bore, the inner diameter nominal and tolerance dimensions are chosen to be smaller than the nominal and tolerance dimensions of the rotor outer diameter in this area that results in a sufficient shrink fit even at operating temperatures. which frictionally fixes the impeller 2 on the rotor 1 in the axial direction x.
  • several, for example, three to five Schrumpfbundstatte 4 in substantially uniformly distributed over the circumference through holes in the shrink collar 2.3 and thus aligned blind holes in the rotor 1 are introduced, thus ensuring the axial position of the impeller 2 on the rotor first
  • Dashed lines the outer contour of a conventional impeller is located, in which the rear wall of the impeller disc in a radius 2.4 'in the shrink band passes. If such an impeller with an operating speed ⁇ (see. Fig. 2 ), the centrifugal forces radially expand the impeller. The more centrifugal force due to their larger outer diameter impeller disk exerts a tilting or bending moment on the shrink collar, which in addition to the impressed centrifugal forces and the radial tensile forces exerted on the rigidly attached to him wheel disk on him, to a widening of the shrink collar and Accordingly, it leads to a reduction of the contact surface between the rotor and shrinkage collar or the normal stresses and the frictional engagement ensured by them.
  • a circumferential groove 3 is instead formed directly on the impeller back 2.2 by the impeller 2 after the prototyping, for example by forging or casting, has been machined by, for example, was stabbed with a Drehmeisel.
  • the circumferential groove 3 has corresponding side walls (left, right in Fig. 1 ), which are substantially perpendicular to the axis of rotation x of the impeller 2, and a rounded groove bottom (bottom in Fig. 1 ) on.
  • the transition of the groove 3 in the radially outer surface of the shrink collar 2.3 also has a radius (not shown) to advance notch effect and risk of injury.
  • Fig. 2 shows in exaggerated representation, the impeller according to the invention in operation, ie at a rotation ⁇ about the axis of rotation x.
  • the impeller disk 2.1 Due to the centrifugal forces, in particular, the impeller disk 2.1 widens with its larger outer diameter due to the blades, represented by the lifting in the left or front impeller region upwards.
  • the forces acting on the shrink collar 2.3 centrifugal forces and transmitted to him radial tensile forces from the impeller 2.1 also expand the shrink collar 2.3.
  • the groove width substantially 0.25 times the total axial length of the shrinkage collar from its right front side to the rear wall 2.2, and its groove depth (top-bottom in Fig.

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

Description

Die Erfindung betrifft ein Laufrad für eine Turbomaschine, insbesondere eine Radialturbomaschine, mit einer Laufradstimseite und einem daran anschließenden Schrumpfbund zum Aufschrumpfen auf einen Rotor der Turbomaschine, sowie eine Turbomaschine mit einem Rotor und einem darauf aufgeschrumpften Laufrad.The invention relates to an impeller for a turbomachine, in particular a radial turbomachine, with an impeller front side and an adjoining shrink collar for shrinking onto a rotor of the turbomachine, and a turbomachine with a rotor and an impeller shrunk thereon.

In Turbomaschinen setzten Laufräder Energie eines sie durchströmenden Fluids und mechanische Energie eines die Laufräder tragenden Rotors aneinander um. In Radialturbomaschinen werden ein oder mehrere Laufräder hierzu quer zur Drehachse des Rotors durchstromt.In turbomachines, impellers convert energy from a fluid passing through them and mechanical energy from a rotor supporting the impellers. In radial turbomachinery, one or more impellers for this purpose are traversed transversely to the axis of rotation of the rotor.

Laufräder sind dabei häufig durch Schrumpfsitze, i.e. ein Übermaß des Rotoraußendurchmessers gegenüber einem Laufradinnendurchmesser, axial auf dem Rotor reibschlüssig festgelegt. Um dabei die Kontaktfläche des Schrumpfsitzes zu vergrößern, weisen bekannte Laufräder an einer oder beiden Stirnseiten Schrumpfbunde auf, i.e. axiale Fortsätze der eigentlichen Laufradscheibe, die einen geringeren Durchmesser aufweisen, Zur Absicherung der sicherheitsrelevanten axialen Festlegung der Laufräder können die Schrumpfbunde zusätzlich mit Schrumpfbundstiften, die fluchtende Bohrungen von Bund und Rotor durchgreifen, gesichert sein.Wheels are often by shrink fit seats, i.e. an excess of the rotor outer diameter relative to a wheel inner diameter, axially fixed friction on the rotor. In order to increase the contact surface of the shrink fit, known wheels on one or both end faces on shrink collars, ie. Axial extensions of the actual impeller disk, which have a smaller diameter, To secure the safety-related axial fixing of the wheels, the shrink collars can be additionally secured with Schrumpfbundstiften that pass through aligned holes of the collar and rotor.

Solche Laufräder werden beispielsweise von den Dokumenten GB 770 004 A , JP S63 26701 U und US 4 697 987 A offenbart.Such wheels are, for example, from the documents GB 770 004 A . JP S63 26701 U and US 4 697 987 A disclosed.

Auf die Laufräder wirken aufgrund der teilweise sehr hohen Drehzahlen, etwa in von Gas oder Dampf durchströmten Kompressoren, Verdichtern oder Turbinen, Fliehkräfte, die unter anderem zu einer Aufweitung des Laufradinnendurchmessers führen und so die durch den Schrumpfsitz aufgeprägten Normalspannungen und mit ihnen den axial festlegenden Relbschluss reduzieren. Schrumpfbundstifte können dabei nachteilig auf Biegung bzw. Scherung beansprucht und durch radiale Mikrobewegungen belastet werden. Beides kann zu einem verschlechterten Betrieb, zu Verschleiß oder sogar zum Versagen der Turbomaschine führen.Due to the sometimes very high speeds, for example in compressors, compressors or turbines flowed through by gas or steam, centrifugal forces act, inter alia, on a widening of the inner diameter of the impeller and thus on the normal stresses imposed by the shrink fit and with them on the axially locking connection to reduce. Shrink collar pins can be adversely affected by bending or shear and loaded by radial micro-movements. Both can lead to degraded operation, wear or even failure of the turbomachine.

Aufgabe der vorliegenden Erfindung ist es, eine verbesserte Turbomaschine zur Verfügung zu stellen.The object of the present invention is to provide an improved turbomachine.

Zur Lösung dieser Aufgabe ist ein Laufrad nach dem Oberbegriff des Anspruchs 1 gemäß dessen kennzeichnendem Merkmal weitergebildt. Anspruch 10 stellt eine Turbomaschine mit einem solchen Laufrad. Die Unteransprüche betreffen vorteilhafte Weiterbildungen.To solve this problem, an impeller according to the preamble of claim 1 according to its characteristic feature further developed. Claim 10 presents a turbomachine with such an impeller. The subclaims relate to advantageous developments.

Ein erfindungsgemäßes Laufrad ist zur Befestigung an einem Rotor einer Turbomaschine, insbesondere einer Radialturbomaschine wie einem Radialkompressor bzw. -verdichter, vorgesehen. Hierzu ist an wenigstens einer Laufradstirnseite, vorzugsweise der stromabwärtigen Rückseite bzw. -wand der die Laufschaufeln tragenden Laufradscheibe, ein Schrumpfbund vorgesehen, der in einer bevorzugten Ausführung einstückig mit der Laufradscheibe ausgebildet ist. Durch, insbesondere thermisches, Aufweiten des Innendurchmessers einer Zentralbohrung des Schrumpfbundes und/oder Komprimieren des zugeordneten Rotoraußendurchmessers wird der Schrumpfbund auf den Rotor aufgeschrumpft.An impeller according to the invention is provided for attachment to a rotor of a turbomachine, in particular a radial turbomachine such as a radial compressor or compressor. For this purpose, a shrink collar is provided on at least one impeller end, preferably the downstream back or wall of the rotor blades carrying the rotor blades, which in one preferred embodiment is integral with the impeller disk. By, in particular thermal, expansion of the inner diameter of a central bore of the shrinkage collar and / or compressing the associated rotor outer diameter of the shrink band is shrunk onto the rotor.

Zwischen der Laufradstimseite und dem mit ihr verbundenen Schrumpfbund ist eine radial außenliegende Umfangsnut ausgebildet. Als Umfangsnut wird insbesondere eine lokale Querschnittsverringerung bezeichnet, wie sie beispielsweise durch Einstechen des sich drehenden Schrumpfbundes mit einem Drehmeißel hergestellt werden kann.Between the Laufradstimseite and the associated shrinkage collar a radially outer circumferential groove is formed. As a circumferential groove in particular a local reduction in cross section is referred to, as can be prepared for example by piercing the rotating shrink collar with a turning tool.

Durch diese Materialschwächung wird eine teilweise Entkoppelung der Laufradscheibe, die aufgrund ihres in der Regel erheblich größeren Außendurchmesseres höheren Fliehkräften ausgesetzt ist, und dem Schrumpfbund, dessen Schrumpfsitz das Laufrad als Ganzes axial festlegt, erreicht. Weitet sich die Laufradscheibe unter Fliehkrafteinfluss, werden insbesondere entsprechende Biegemomente, die zu einer Aufweitung des Schrumpfbundes führen, in der insoweit gelenkähnlich wirkenden Umfangsnut nicht oder nur reduziert in den Schrumpfbund eingeleitet. Dies kann dazu führen, dass die axiale Kontaktlänge zwischen Schrumpfbund und Rotor sich im Betrieb vorteilhafterweise weniger reduziert, da der Schrumpfbund sich nur in einem kürzeren Abschnitt aufweiset. Das kann es insbesondere ermöglichen,By this material weakening is a partial decoupling of the impeller disc, which is exposed to higher centrifugal forces due to their usually much larger outer diameter, and the shrink collar, the shrink fit, the impeller sets axially as a whole achieved. Widened the impeller disc under the influence of centrifugal force, in particular corresponding bending moments, which lead to a widening of the shrinkage, in the extent far joint-like acting circumferential groove not or only reduced introduced into the shrink collar. This can lead to the fact that the axial contact length between the shrinkage collar and the rotor during operation advantageously less reduced, since the shrink band is only in a shorter section. This can in particular enable

Schrumpfbundstifte in Bereichen des Schrumpfbundes anzuordnen, welche sich nicht oder weniger aufweiten als herkömmlich, ohne Nut in die Laufradscheibe übergehende Schrumpfbunde. Solche Schrumpfbundstifte werden dann vorteilhafterweise weniger belastet.To arrange shrink collars in areas of the shrink bundle, which do not expand or less than conventional, without groove in the impeller disc passing shrinkage collars. Such Schrumpfbundstifte are then advantageously less burdened.

Überraschenderweise führt also eine vermeintliche Schwächung des Laufrades durch eine lokale Materialverringerung In Form einer radialen Einschnürung zwischen Laufradscheibe und Schrumpfbund zu einem verbesserten Schrumpfsitz des Schrumpfbundes im Betrieb. Diese Vorteile überwiegen die mit der insoweit elastischeren Anbindung der Laufradscheibe an den Schrumpfbund einhergehende größere radiale Aufweitung der Laufradscheibe insbesondere in einem Dichtungsbereich sowie die geringeren übertragbaren Leistungen.Surprisingly, therefore, leads a supposed weakening of the impeller by a local material reduction in the form of a radial constriction between the impeller disc and shrink collar to an improved shrink fit of the shrink collar during operation. These advantages outweigh the greater radial widening of the impeller disc, in particular in a sealing region, and the lower transferable services, which are accompanied by the elastic connection of the impeller disc to the shrink collar.

Die Umfangsnut kann in fertigungs-, montage-, festigkeitstechnischer, thermodynamischer und/oder dynamischer Hinsicht optimiert sein. So ist beispielsweise eine Umfangsnut, deren Seitenwände im Wesentlichen senkrecht zur Drehachse des Laufrades orientiert sind, besonders einfach, beispielsweise spanabhebenden, herstellbar. Abgerundete Übergänge bzw. Kanten zwischen Nutseitenwände und Nutgrund und/oder der radial äußeren Mantelfläche des Schrumpfbundes verringern gleichermaßen die Verletzungsgefahr bei der Montage als auch die Kerbwirkung mit entsprechendem Einfluss auf die Festigkeit, insbesondere die Dauerfestigkeit und Anfälligkeit gegen Schwingungen. Eine entsprechende Bemaßung von Nutbreite und/oder -tiefe beeinflusst den Wärmeübergang zwischen Laufradscheibe und Schrumpfbund im Betrieb und beim Aufschrumpfen sowie die Steifigkeit der Anbindung der 1 aufradscheibe an den Schrumpfbund und damit das Schwingungsverhalten und die Aufweitung der Laufradscheibe unter Fliehkraft und Axialschub des Arbeisfluides.The circumferential groove can be optimized in terms of production, assembly, strength, thermodynamic and / or dynamic aspects. Thus, for example, a circumferential groove, whose side walls are oriented substantially perpendicular to the axis of rotation of the impeller, particularly simple, for example, cutting, produced. Rounded transitions or edges between groove side walls and groove bottom and / or the radially outer surface of the shrink collar reduce both the risk of injury during assembly and the notch effect with a corresponding impact on the strength, in particular the fatigue strength and susceptibility to vibration. A corresponding dimensioning of groove width and / or depth influences the heat transfer between the impeller disc and shrink collar during operation and during shrinking and the rigidity of the connection of the 1 aufradscheibe to the shrink collar and thus the vibration behavior and expansion of the impeller disc under centrifugal force and axial thrust of the working fluid.

Erfindungsgemäß ist die Umfangsnut radial mehrfach abgestuft, i.e. in Richtung der Drehachse des Laufrades weist sie bereichsweise unterschiedliche Außendurchmesser auf Zusätzlich ist es auch möglich, dass die Umfangsnut eine gegen die Drehachse geneigte Mantelfläche und/oder eine gekrümmte Mantelfläche aufweist. Besonders günstige fertigungs-, montage-, und festigkeitstechnische, thermodynamische und dynamische Eigenschaften ergeben sich bei radialen Nuttiefen in einem Bereich zwischen dem 0,1-fachen und dem 0,99-fachen, insbesondere dem 0,3-fachen und dem 0,7-fachen, bevorzugt dem 0,5-fachen und dem 0,65-fachen, vorzugsweise etwa dem 0,55-fachen der radialen Höhe des Schrumpfbundes. i.e. des maximalen radialen Abstandes zwischen Innen- und Außendurchmesser des Schrumpfbundes.According to the invention, the circumferential groove is graduated radially several times, ie in the direction of the axis of rotation of the impeller, it has regions of different outer diameter. In addition, it is also possible for the circumferential groove to have a lateral surface inclined towards the axis of rotation and / or a curved lateral surface. Particularly favorable manufacturing, assembly, and strength engineering, thermodynamic and dynamic properties arise in radial Groove depths in a range between 0.1 times and 0.99 times, in particular 0.3 times and 0.7 times, preferably 0.5 times and 0.65 times, preferably about 0.55 times the radial height of the shrinkage collar. ie the maximum radial distance between inner and outer diameter of the shrinkage collar.

Bevorzugt ist die Umfangsnut im Wesentlichen unmittelbar an der Laufradstirnseite bzw. der Laufradscheibe angeordnet, um so einen größeren zusammenhängenden axialen Sitz des verbleibenden Schrumpfbundes zu erreichen.Preferably, the circumferential groove is arranged substantially directly on the impeller front side or the impeller disk so as to achieve a larger contiguous axial seat of the remaining shrink collars.

Weitere Vorteile und Merkmale ergeben sich aus den Unteransprüchen und dem Ausführungsbeispiel. Hierzu zeigt, teilweise schematisiert,

Fig. 1:
einen Teil eines Rotors mit einem aufgeschrumpften Laufrad nach einer Ausführung der vorliegenden Erfindung im Meridian- bzw. Längsschnitt bei Stillstand; und
Fig. 2:
das Laufrad nach Fig. 1 im Betrieb.
Further advantages and features emerge from the subclaims and the exemplary embodiment. This shows, partially schematized,
Fig. 1:
a portion of a rotor with a shrunk-wheel according to an embodiment of the present invention in meridian or longitudinal section at a standstill; and
Fig. 2:
the impeller after Fig. 1 operational.

Fig. 1 zeigt im Meridianschnitt einen Teil eines Rotors 1 eines Radiakompressors, auf dem ein Laufrad 2 befestigt ist. Dieses weist eine Laufradscheibe 2.1 und einen integral mit dieser ausgebildeten Schtumpfbund 2.3 auf, der an der stromabwärtigen, von den Laufschaufeln abgewandten Rückseite 2.2 der Laufradscheibe 2.1 angeordnet ist. Fig. 1 shows in meridian section a part of a rotor 1 of a radio compressor, on which an impeller 2 is fixed. This has an impeller disc 2.1 and an integral with this Schtumpfbund 2.3, which is disposed on the downstream, facing away from the blades rear 2.2 of the impeller disc 2.1.

Das Laufrad 2 weist eine durchgehende, zylindrische Zentralbohrung auf, deren Innendurchmesser-Nenn- und Toleranzmaße derart kleiner gewählt sind als die Nenn- und Toleranzmaße des Rotoraußendurchmessers in diesem Bereich, dass sich auch bei Betriebstemperaturen ein ausreichender Schrumpfsitz ergibt. der das Laufrad 2 in axialer Richtung x reibschlüssig auf dem Rotor 1 festlegt. Zusätzlich sind mehrere, beispielsweise drei bis fünf Schrumpfbundstifte 4 in im Wesentlichen gleichmäßig über dem Umfang verteilte Durchgangsbohrungen im Schrumpfbund 2.3 und damit fluchtenden Sackbohrungen im Rotor 1 eingeführt und sichern so die axiale Lage des Laufrades 2 auf dem Rotor 1.The impeller 2 has a continuous, cylindrical central bore, the inner diameter nominal and tolerance dimensions are chosen to be smaller than the nominal and tolerance dimensions of the rotor outer diameter in this area that results in a sufficient shrink fit even at operating temperatures. which frictionally fixes the impeller 2 on the rotor 1 in the axial direction x. In addition, several, for example, three to five Schrumpfbundstifte 4 in substantially uniformly distributed over the circumference through holes in the shrink collar 2.3 and thus aligned blind holes in the rotor 1 are introduced, thus ensuring the axial position of the impeller 2 on the rotor first

Strichliert ist die Außenkontur eines herkömmlichen Laufrades eingezeichnet, bei dem die Rückwand der Laufradscheibe in einem Radius 2.4' in den Schrumpfbund übergeht. Wird ein solches Laufrad mit einer Betriebsdrehzahl Ω (vgl. Fig. 2) beaufschlagt, weiten die Fliehkräfte das Laufrad radial auf. Die aufgrund ihres größeren Außendurchmessers stärker fliehkraftbelastete Laufradscheibe übt dabei ein Kipp- bzw. Biegemoment auf den Schrumpfbund aus, was zusätzlich zu den ihm eingeprägten Fliehkräften und den radialen Zugkräften, die die steif an ihn gefesselte Laufradscheibe auf ihn ausübt, zu einer Aufweitung des Schrumpfbundes und dementsprechend zu einer Verringerung der Kontaktfläche zwischen Rotor und Schrumpfbund bzw. der Normalspannungen und der durch diese gewährleisteten Reibschluss führt.Dashed lines the outer contour of a conventional impeller is located, in which the rear wall of the impeller disc in a radius 2.4 'in the shrink band passes. If such an impeller with an operating speed Ω (see. Fig. 2 ), the centrifugal forces radially expand the impeller. The more centrifugal force due to their larger outer diameter impeller disk exerts a tilting or bending moment on the shrink collar, which in addition to the impressed centrifugal forces and the radial tensile forces exerted on the rigidly attached to him wheel disk on him, to a widening of the shrink collar and Accordingly, it leads to a reduction of the contact surface between the rotor and shrinkage collar or the normal stresses and the frictional engagement ensured by them.

Bei dem erfindungsgemäßen Laufrad ist stattdessen unmittelbar am Laufradrücken 2.2 anstelle des Radius 2.4' eine Umfangsnut 3 ausgebildet, indem das Laufrad 2 nach dem Urformen, zum Beispiel durch Schmieden oder Gießen, spanabhebende bearbeitet wurde, indem beispielsweise mit einem Drehmeisel eingestochen wurde. Die Umfangsnut 3 weist dementsprechend Seitenwände (links, rechts in Fig. 1), die im Wesentlichen senkrecht zur Drehachse x des Laufrades 2 sind, und einen gerundeten Nutgrund (unten in Fig. 1) auf. Der Übergang der Nut 3 in die radial äußere Mantelfläche des Schrumpfbundes 2.3 weist ebenfalls einen Radius auf (nicht dargestellt), um Kerbwirkung und Verletzungsgefahr zu vorringern.In the impeller according to the invention, instead of the radius 2.4 ', a circumferential groove 3 is instead formed directly on the impeller back 2.2 by the impeller 2 after the prototyping, for example by forging or casting, has been machined by, for example, was stabbed with a Drehmeisel. The circumferential groove 3 has corresponding side walls (left, right in Fig. 1 ), which are substantially perpendicular to the axis of rotation x of the impeller 2, and a rounded groove bottom (bottom in Fig. 1 ) on. The transition of the groove 3 in the radially outer surface of the shrink collar 2.3 also has a radius (not shown) to advance notch effect and risk of injury.

Fig. 2 zeigt in übertriebener Darstellung das erfindungsgemäße Laufrad im Betrieb, i.e. bei einer Rotation Ω um die Drehachse x. Aufgrund der Fliehkräfte weitet sich insbesondere die Laufradscheibe 2.1 mit ihrem aufgrund der Laufschaufeln größeren Außendurchmesser, dargestellt durch das Abheben im linken bzw. vorderen Laufradbereich nach oben. Die auf den Schrumpfbund 2.3 wirkenden Fliehkräfte sowie auf ihn übertragene radiale Zugkräfte von der Laufradscheibe 2.1 weiten auch den Schrumpfbund 2.3. Da jedoch die Umfangsnut 3, deren Nutbreite (links-rechts in Fig. 1) im Wesentlichen das 0,25-fache der gesamten axialen Länge des Schrumpfbundes von seiner rechten Stirnseite bis zur Rückwand 2.2, und dessen Nuttiefe (oben-unten in Fig. 1) im Wesentlichen das 0,65-fache der radialen Höhe des Schrumpfbundes von seinem Innen- zu seinem Außendurchmesser beträgt, gelenkartig wirkt, übt die Laufradscheibe 2.1 nur ein geringes Kipp- bzw. Biegemoment auf den Schrumpfbund 2.3 aus, so dass sich dessen tragende Schrumpfsitzlänge weniger verringert als bei herkömmlichen Laufrädern. Fig. 2 shows in exaggerated representation, the impeller according to the invention in operation, ie at a rotation Ω about the axis of rotation x. Due to the centrifugal forces, in particular, the impeller disk 2.1 widens with its larger outer diameter due to the blades, represented by the lifting in the left or front impeller region upwards. The forces acting on the shrink collar 2.3 centrifugal forces and transmitted to him radial tensile forces from the impeller 2.1 also expand the shrink collar 2.3. However, since the circumferential groove 3, the groove width (left-right in Fig. 1 ) substantially 0.25 times the total axial length of the shrinkage collar from its right front side to the rear wall 2.2, and its groove depth (top-bottom in Fig. 1 ) is substantially the 0.65 times the radial height of the shrinkage collar from its inner to its outer diameter is hinged, exercises the impeller 2.1 only a slight tilting or bending moment on the Shrink collar 2.3, so that its bearing shrink fit length less reduced than conventional wheels.

Dementsprechend wird durch die Einschnürung 3 ein verbesserter Schrumpfsitz im Betrieb erreicht. Insbesondere werden die im hinteren Bereich angeordneten Schrumpfbundstifte 4 weniger beansprucht und so die Sicherheit erhöht. Eine gegenüber herkömmlichen Laufrädern größere radiale Aufweitung am vorderen Laufradbereich (links in Fig. 1) ist demgegenüber vernachlässigbar bzw. durch entsprechende Dimensionierung eines Dichtungsdurchmessers (nicht dargestellt) zu kompensieren.Accordingly, an improved shrink fit during operation is achieved by the constriction 3. In particular, the arranged in the rear area Schrumpfbundstifte 4 are less stressed and thus increases security. A larger radial expansion at the front wheel area compared to conventional wheels (left in Fig. 1 ) is in contrast negligible or by appropriate dimensioning of a seal diameter (not shown) to compensate.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Rotorrotor
22
LaufradWheel
2.12.1
Laufradscheibewheel disc
2.22.2
Laufradrücken (Laufradstirnseite)Impeller back (impeller front side)
2.32.3
Schrumpfbundshrink Bund
2.4'2.4 '
Radius (Stand der Technik)Radius (prior art)
33
Umfangsnutcircumferential groove
44
SchrumpfbundstiftShrink crayon

Claims (10)

  1. An impeller (2) for a turbomachine, in particular a radial turbomachine, with an impeller disc (2.1) carrying moving blades and a shrink collar (2.3) following the impeller face end (2.2), with a supporting shrink collar seat length, wherein the shrink collar (2.3) is suitable for shrinking onto a rotor (1) (of the turbomachine), wherein between impeller face end (2.2) of the impeller disc (2.1) and the shrink collar (2.3) connected to the same a circumferential groove (3) located radially outside is formed, characterized in that the circumferential groove (3) is radially stepped multiple times.
  2. The impeller according to Claim 1, characterized in that the shrink collar (2.3) is arranged on a downstream back wall (2.2) of the impeller (2).
  3. The impeller according to any one of the preceding claims, characterized in that the shrink collar is unitarily formed with the impeller disc (2.1) of the impeller.
  4. The impeller according to any one of the preceding claims, characterized in that the circumferential groove (3) is directly formed on the impeller face end (2.2).
  5. The impeller according to any one of the preceding claims, characterized in that the groove depth in radial direction amounts to at least 0.1 times, in particular at least 0.3 times and preferably at least 0.5 times the radial height of the shrink collar; and/or in that the groove depth in radial direction amounts to a maximum of 0.99 times, in particular a maximum of 0.7 times and preferably a maximum of 0.65 times the radial height of the shrink collar.
  6. The impeller according to any one of the preceding claims, characterized by at least one bore for receiving a shrink collar pin (4), which is arranged between the circumferential groove (3) and a face end of the shrink collar (2.3).
  7. The impeller according to any one of the preceding claims, characterized in that the circumferential groove (3) is rounded radially inside and/or outside.
  8. The impeller according to any one of the preceding claims, characterized in that the circumferential groove (3) is produced by casting, forming and/or chip-removing processing, in particular plunging with a plunging tool.
  9. The impeller according to any one of the preceding claims, characterized in that the circumferential groove (3) has an outer surface that is curved and/or inclined towards the axis of rotation of the rotor (1).
  10. The turbomachine, in particular radial turbomachine, with an impeller (2) according to any one of the preceding claims.
EP10708100.2A 2009-07-04 2010-01-25 Turbomachine impeller Not-in-force EP2452076B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009031737A DE102009031737A1 (en) 2009-07-04 2009-07-04 Impeller for a turbomachine
PCT/DE2010/050002 WO2011003409A1 (en) 2009-07-04 2010-01-25 Rotor disk for a turbo machine

Publications (2)

Publication Number Publication Date
EP2452076A1 EP2452076A1 (en) 2012-05-16
EP2452076B1 true EP2452076B1 (en) 2017-03-08

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EP10708100.2A Not-in-force EP2452076B1 (en) 2009-07-04 2010-01-25 Turbomachine impeller

Country Status (6)

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US (1) US9316234B2 (en)
EP (1) EP2452076B1 (en)
JP (1) JP5613764B2 (en)
CN (1) CN102510953B (en)
DE (1) DE102009031737A1 (en)
WO (1) WO2011003409A1 (en)

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KR101705664B1 (en) * 2010-02-19 2017-02-10 보르그워너 인코퍼레이티드 Turbine wheel and method for the production thereof
JP5449117B2 (en) 2010-12-08 2014-03-19 三菱重工業株式会社 Rotating machine
JP5606358B2 (en) 2011-02-24 2014-10-15 三菱重工業株式会社 Impeller, rotor provided with the same, and method for manufacturing impeller
JP5787599B2 (en) * 2011-04-28 2015-09-30 三菱重工業株式会社 Impeller
JP2013047479A (en) 2011-08-29 2013-03-07 Mitsubishi Heavy Ind Ltd Impeller and rotary machine with the same, and method for manufacturing impeller
JP5907723B2 (en) 2011-12-26 2016-04-26 三菱重工業株式会社 Manufacturing method of rotating machine
JP5967966B2 (en) * 2012-02-13 2016-08-10 三菱重工コンプレッサ株式会社 Impeller and rotating machine equipped with the same
DE102013018005A1 (en) 2013-11-29 2015-06-03 Mtu Friedrichshafen Gmbh Shaft-hub connection
DE102014215089A1 (en) * 2014-07-31 2016-02-04 Ksb Aktiengesellschaft Flow guiding component
JP6536417B2 (en) * 2016-01-20 2019-07-03 株式会社豊田自動織機 Turbocharger
FR3047075B1 (en) * 2016-01-27 2018-02-23 Safran Aircraft Engines REVOLUTION PIECE FOR TURBINE TEST BENCH OR FOR TURBOMACHINE, TURBINE TESTING BENCH COMPRISING THE TURBINE, AND PROCESS USING THE SAME

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JPS6326701U (en) * 1986-08-05 1988-02-22

Also Published As

Publication number Publication date
US9316234B2 (en) 2016-04-19
EP2452076A1 (en) 2012-05-16
CN102510953B (en) 2015-04-29
JP5613764B2 (en) 2014-10-29
US20120189373A1 (en) 2012-07-26
JP2012531554A (en) 2012-12-10
WO2011003409A1 (en) 2011-01-13
DE102009031737A1 (en) 2011-07-21
CN102510953A (en) 2012-06-20

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