EP2452076A1 - Roue à aubes pour une turbomachine - Google Patents
Roue à aubes pour une turbomachineInfo
- Publication number
- EP2452076A1 EP2452076A1 EP10708100A EP10708100A EP2452076A1 EP 2452076 A1 EP2452076 A1 EP 2452076A1 EP 10708100 A EP10708100 A EP 10708100A EP 10708100 A EP10708100 A EP 10708100A EP 2452076 A1 EP2452076 A1 EP 2452076A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- circumferential groove
- collar
- shrink
- impeller according
- 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
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
- impellers intermix energy from a fluid passing through them and mechanical energy from a rotor supporting the impellers.
- In Radsalturbomaschinen one or more wheels are transverse thereto
- Rotational axis of the rotor flows through.
- Wheels are often by shrink fit seats, i.e. an excess of
- Impeller disk which have a smaller diameter.
- shrink collars should be secured with shrink collars that pass through aligned holes in the collar and rotor.
- Shrink collar pins can be disadvantageously stressed bending or shear and loaded by radial micro-movements. Both can lead to degraded operation, wear or even failure of the turbomachine.
- Object of the present invention is. an improved turbomachine to steep.
- an impeller according to the preamble of claim 1 according to its characterizing Merkmai further developed claim 12 provides a turbomachine with such an impeller.
- Claim 13 a method for
- An erf ⁇ ndungsgemä ⁇ es impeller is for attachment to a rotor of a
- Turbomachine in particular, of a radial turbomachine such as a
- a shrink collar is provided on at least one impeller end, preferably the downstream back or wall of the Laufschaufein carrying impeller disc, which is formed in one preferred embodiment integral with the impeller disc.
- a radially outer circumferential groove is formed between the impeller end side and the shrink band connected to it.
- Circumferential groove is in particular an iokaie cross-sectional reduction referred to, as can be prepared for example by piercing the rotating shrink collar with a DrehmeiSel.
- Impeller disc which due to their m usually much larger
- Shrinkband lead in the extent geienkähntich acting circumferential groove not or only reduced introduced in Schren shrinkage collar. This can lead to the axial contact length between shrink collar and rotor advantageously being less reduced during operation, since the shrink band widens only in a shorter section. That can make it possible in particular.
- shrink collars in areas of Schrumpfbundes that does not widen or less than conventional, without groove m the impeller disc passing shrink collars. Such shrink collars are then
- the circumferential groove can in Ferttgungs-, montage-, strength-technical,
- a circumferential groove the side walls are oriented substantially perpendicular to the axis of rotation of the impeller, particularly simple «eg machined, heritable Rounded transitions or edges between Nutrich treat and groove bottom and / or the radially outer surface of the shrink joint equally reduce the danger of Verietzungs in the
- the circumferential groove can also be graduated radially one or more times, i. in the direction of the axis of rotation of the impeller
- the circumferential groove may have a lateral surface inclined towards the axis of rotation and / or a curved lateral surface.
- thermodynamic and dynamic properties arise in radial Other depths in the range between 0.1 times and 0.99 times, in particular 0.3 times and 0.7 times, preferably at 6 times and 0.85 times, preferably approximately 0.55 times the radial height of the shrinkage collar, ie the maximum radial distance between the inner and outer diameters of the shrinkage collar.
- the circumferential groove is substantially directly on the circumferential groove
- Impeller front side or the impeller disc arranged so as to achieve a larger contiguous axial seat of the remaining Schrumpfbundes.
- FIG. 1 shows a part of a rotor with a shrunk-on impeller according to an embodiment of the present invention in meridian or longitudinal section at standstill;
- Fig. 2 the impeller of Fig. 1 in operation.
- 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 integrally formed with this Schrumpfbund 2.3, on the downstream, facing away from the Laufschaufein back 2.2 of
- Impeller disk 2.1 is arranged.
- the impeller 2 has a continuous, cylindrical Zentraibohrung whose inner diameter nominal and tolerance dimensions are chosen so smaller than the nominal and tolerance dimensions of Rotorau & diameters in this area, that even at operating temperatures sufficient shrink fit results, the impeller 2 in axial Direction x frictionally on the rotor 1 defines.
- Laufradröcken 2.2 instead of the radius 2.4 'a circumferential groove 3 is formed by the impeller 2 has been machined after the primary molding, for example by forging or casting, for example, was pierced by a Drehmeisei.
- the circumferential groove 3 accordingly has 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).
- the transition of the groove 3 in the radially outer surface of the shrink collar 2.3 also has a radius (not shown), notch effect and
- Fig. 2 shows an exaggerated representation of the impeller according to the invention in
- Blades larger outer diameter represented by the lifting in the left or front impeller area upwards.
- Impeller disc 2.1 also widen the shrink collar 2.3. However, since the
- circumferential groove 3 whose groove width (left-right in Fig. 1) is substantially 0.25 times the total axial length of the shrink collar from its right end to the rear wall 2.2, uus the groove depth (top-bottom in Fig. 1) in Substantially 0.85 times the radial height of the shrinkage collar from its inner to its outer diameter is articulated, exercises the
- Impeller 2.1 only a slight tilting or bending moment on the Schr ⁇ mpfbund 2.3 off, so that its supporting Schrumpfsitzin less reduced than conventional La ⁇ fraten.
- the constriction 3 achieves an improved butt seat during operation.
- the rear-mounted Schrumpfbundsttfte 4 are less stressed wv $ so increases security.
- larger radial revaluation at the front wheel area is negligible or compensated by appropriate dimensioning of a sealing diameter (not shown).
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)
Abstract
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 true EP2452076A1 (fr) | 2012-05-16 |
EP2452076B1 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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112011100606B4 (de) * | 2010-02-19 | 2022-12-08 | Borgwarner Inc. | Turbinenrad und Verfahren zu seiner Herstellung |
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 |
Family Cites Families (16)
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 |
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 |
JPH0417762Y2 (fr) | 1985-06-19 | 1992-04-21 | ||
JPS6326701U (fr) * | 1986-08-05 | 1988-02-22 | ||
DE29702119U1 (de) * | 1997-02-07 | 1997-04-24 | Aktiengesellschaft Kühnle, Kopp & Kausch, 67227 Frankenthal | 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 |
DE10101165C2 (de) * | 2001-01-12 | 2003-06-05 | Man B & W Diesel Ag | Befestigungsvorrichtung für ein radial durchströmtes Verdichterrad |
US7001155B2 (en) * | 2002-07-30 | 2006-02-21 | Honeywell International, Inc. | Compressor impeller with stress riser |
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 |
CN201236724Y (zh) * | 2008-07-17 | 2009-05-13 | 鳳城太平洋神龍增壓器有限公司 | 一种轻质钛合金涡轮增压器 |
-
2009
- 2009-07-04 DE DE102009031737A patent/DE102009031737A1/de not_active Withdrawn
-
2010
- 2010-01-25 WO PCT/DE2010/050002 patent/WO2011003409A1/fr active Application Filing
- 2010-01-25 JP JP2012518018A patent/JP5613764B2/ja not_active Expired - Fee Related
- 2010-01-25 EP EP10708100.2A patent/EP2452076B1/fr not_active Not-in-force
- 2010-01-25 US US13/382,111 patent/US9316234B2/en not_active Expired - Fee Related
- 2010-01-25 CN CN201080030308.0A patent/CN102510953B/zh not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US20120189373A1 (en) | 2012-07-26 |
EP2452076B1 (fr) | 2017-03-08 |
JP5613764B2 (ja) | 2014-10-29 |
CN102510953A (zh) | 2012-06-20 |
JP2012531554A (ja) | 2012-12-10 |
WO2011003409A1 (fr) | 2011-01-13 |
DE102009031737A1 (de) | 2011-07-21 |
US9316234B2 (en) | 2016-04-19 |
CN102510953B (zh) | 2015-04-29 |
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