EP2452076B1 - Rotor de turbomachine - Google Patents

Rotor de turbomachine 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
Authority
EP
European Patent Office
Prior art keywords
impeller
shrink
collar
circumferential groove
shrink collar
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.)
Not-in-force
Application number
EP10708100.2A
Other languages
German (de)
English (en)
Other versions
EP2452076A1 (fr
Inventor
Christoph Lange
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Energy Solutions SE
Original Assignee
MAN Diesel and Turbo SE
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP2452076A1 publication Critical patent/EP2452076A1/fr
Application granted granted Critical
Publication of EP2452076B1 publication Critical patent/EP2452076B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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.

Landscapes

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

Claims (10)

  1. Rotor (2) pour une turbomachine, notamment une turbomachine radiale, comportant un disque de rotor (2.1) supportant des pales de rotor et une frette (2.3) se rattachant à son côté frontal de rotor (2.2), comportant une longueur d'assise de frette, dans lequel la frette (2.3) convient pour un frettage sur un rotor (1) de la turbomachine, dans lequel entre le côté frontal du rotor (2.2) du disque de rotor de rotor (2.1) et la frette (2.3) qui lui est reliée, une rainure circonférentielle (3) radiale située le plus à l'extérieur est réalisée, caractérisé en ce que la rainure circonférentielle (3) présente des gradins radiaux multiples.
  2. Rotor selon la revendication 1, caractérisé en ce que la frette (2.3) est disposée sur une paroi arrière (2.2) en aval du rotor (2).
  3. Rotor selon une des revendications précédentes, caractérisé en ce que la frette est réalisée en un seul tenant avec le disque de rotor (2.1) du rotor.
  4. Rotor selon une des revendications précédentes, caractérisé en ce que la rainure circonférentielle (3) est réalisée directement sur le côté frontal de rotor (2.2).
  5. Rotor selon une des revendications précédentes, caractérisé en ce que la profondeur de rainure dans la direction radiale correspond au moins à 0,1 fois, notamment au moins 0,3 fois et de préférence au moins 0,5 fois la hauteur radiale de la frette ; et/ou en ce que la profondeur de rainure dans la direction radiale correspond au maximum à 0,99 fois, notamment au maximum à 0,7 fois et de préférence au maximum à 0,65 fois la hauteur radiale de la frette.
  6. Rotor selon une des revendications précédentes, caractérisé par au moins un alésage pour recevoir une goupille de frette (4), qui est disposé entre la rainure circonférentielle (3) et un côté frontal de la frette (2.3).
  7. Rotor selon une des revendications précédentes, caractérisé en ce que la rainure circonférentielle (3) est arrondie radialement à l'intérieur et/ou à l'extérieur.
  8. Rotor selon une des revendications précédentes, caractérisé en ce que la rainure circonférentielle (3) est fabriquée par transformation primaire, façonnage et/ou usinage avec enlèvement de copeaux, notamment piquage avec un burin.
  9. Rotor selon une des revendications précédentes, caractérisé en ce que la rainure circonférentielle (3) présente une surface de gaine incurvée et/ou inclinée contre l'axe de rotation du rotor (1).
  10. Turbomachine, notamment turbomachine radiale, comportant un rotor (2) selon une des revendications précédentes.
EP10708100.2A 2009-07-04 2010-01-25 Rotor de turbomachine Not-in-force EP2452076B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009031737A DE102009031737A1 (de) 2009-07-04 2009-07-04 Laufrad für eine Turbomaschine
PCT/DE2010/050002 WO2011003409A1 (fr) 2009-07-04 2010-01-25 Roue à aubes pour une turbomachine

Publications (2)

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

Family

ID=42115111

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10708100.2A Not-in-force EP2452076B1 (fr) 2009-07-04 2010-01-25 Rotor de turbomachine

Country Status (6)

Country Link
US (1) US9316234B2 (fr)
EP (1) EP2452076B1 (fr)
JP (1) JP5613764B2 (fr)
CN (1) CN102510953B (fr)
DE (1) DE102009031737A1 (fr)
WO (1) WO2011003409A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011102984A2 (fr) * 2010-02-19 2011-08-25 Borgwarner Inc. Roue de turbine et son procédé de production
JP5449117B2 (ja) 2010-12-08 2014-03-19 三菱重工業株式会社 回転機械
JP5606358B2 (ja) 2011-02-24 2014-10-15 三菱重工業株式会社 インペラ及びこれを備えたロータ並びにインペラの製造方法
JP5787599B2 (ja) * 2011-04-28 2015-09-30 三菱重工業株式会社 インペラ
JP2013047479A (ja) 2011-08-29 2013-03-07 Mitsubishi Heavy Ind Ltd インペラ及びこれを備えた回転機械並びにインペラの製造方法
JP5907723B2 (ja) 2011-12-26 2016-04-26 三菱重工業株式会社 回転機械の製造方法
JP5967966B2 (ja) * 2012-02-13 2016-08-10 三菱重工コンプレッサ株式会社 インペラ及びこれを備えた回転機械
DE102013018005A1 (de) 2013-11-29 2015-06-03 Mtu Friedrichshafen Gmbh Wellen-Naben-Verbindung
DE102014215089A1 (de) 2014-07-31 2016-02-04 Ksb Aktiengesellschaft Strömungsführendes Bauteil
JP6536417B2 (ja) * 2016-01-20 2019-07-03 株式会社豊田自動織機 ターボチャージャ
FR3047075B1 (fr) * 2016-01-27 2018-02-23 Safran Aircraft Engines Piece de revolution pour banc d'essai de turbine ou pour turbomachine, banc d'essais de turbines comprenant ladite piece, et procede les utilisant

Citations (3)

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Publication number Priority date Publication date Assignee Title
GB770004A (en) * 1954-05-11 1957-03-13 Rover Co Ltd Means for mounting a rotor on a shaft
US4697987A (en) * 1985-06-19 1987-10-06 Mitsubishi Jukogyo Kabushiki Kaisha Rotary machine having an impeller with a sleeve fixedly mounted to a shaft
JPS6326701U (fr) * 1986-08-05 1988-02-22

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GB1191110A (en) * 1967-10-13 1970-05-06 Ckd Praha Improvements in or relating to Centrifugal Compressors
DE2457231C2 (de) 1974-12-04 1976-11-25 Motoren Turbinen Union Laufrad fuer eine schnellaufende turbomaschine
DE2621201C3 (de) 1976-05-13 1979-09-27 Maschinenfabrik Augsburg-Nuernberg Ag, 8900 Augsburg Laufrad für eine Strömungsmaschine
DE29702119U1 (de) * 1997-02-07 1997-04-24 Kuehnle Kopp Kausch Ag Läuferwelle mit Verdichterrad
DE19736333C1 (de) * 1997-08-21 1999-03-04 Man B & W Diesel Ag Befestigung eines Laufrades einer Strömungsmaschine an einer Welle
JP2000054954A (ja) 1998-08-07 2000-02-22 Toyota Autom Loom Works Ltd 可変容量圧縮機用ピストンの製造方法
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GB2392477A (en) * 2002-08-24 2004-03-03 Alstom Turbocharger
JP2004084816A (ja) * 2002-08-27 2004-03-18 Nsk Ltd トロイダル型無段変速機
DE102005037739A1 (de) * 2005-08-10 2007-02-15 Daimlerchrysler Ag Verbundrotor für Abgasturbolader mit Titanaluminid-Rädern
DE102007012641A1 (de) * 2007-03-16 2008-09-18 Daimler Ag Laufzeug für einen Abgasturbolader
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Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB770004A (en) * 1954-05-11 1957-03-13 Rover Co Ltd Means for mounting a rotor on a shaft
US4697987A (en) * 1985-06-19 1987-10-06 Mitsubishi Jukogyo Kabushiki Kaisha Rotary machine having an impeller with a sleeve fixedly mounted to a shaft
JPS6326701U (fr) * 1986-08-05 1988-02-22

Also Published As

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

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