WO2002090776A2 - Rotor disk - Google Patents

Rotor disk Download PDF

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Publication number
WO2002090776A2
WO2002090776A2 PCT/EP2002/004920 EP0204920W WO02090776A2 WO 2002090776 A2 WO2002090776 A2 WO 2002090776A2 EP 0204920 W EP0204920 W EP 0204920W WO 02090776 A2 WO02090776 A2 WO 02090776A2
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
blades
full
clutch
wheel
Prior art date
Application number
PCT/EP2002/004920
Other languages
German (de)
French (fr)
Other versions
WO2002090776A3 (en
Inventor
Andreas Blank
Günther Kiefer
Wolfgang Ladner
Michael Brandes
Original Assignee
Mtu Friedrichshafen Gmbh
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 Mtu Friedrichshafen Gmbh filed Critical Mtu Friedrichshafen Gmbh
Priority to US10/476,990 priority Critical patent/US20040202539A1/en
Priority to EP02769136A priority patent/EP1387962A2/en
Publication of WO2002090776A2 publication Critical patent/WO2002090776A2/en
Publication of WO2002090776A3 publication Critical patent/WO2002090776A3/en

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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/662—Balancing of rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • 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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Definitions

  • the invention relates to an impeller according to the preamble of the first claim.
  • impellers are used as radial fans or as
  • Compressor wheel used for an exhaust gas turbocharger The problem with these wheels is the noise, which is often perceived as unpleasant.
  • a common measure for noise reduction is to equip the impeller with full and splinter blades. Such an embodiment is known from EP 0 439 267 B1.
  • the number of full blades on this impeller may not be the same as the number of fragment blades.
  • the object on which the invention is based is seen in further reducing the noise emission of an impeller.
  • the solid blades and splinter blades be arranged at different angular distances and in a different order. This significantly reduces the noise level. Thanks to the constructive measures, the sound power is distributed over several individual tones, the intensity of which is correspondingly lower. Another advantage is that the efficiency and power consumption of the impeller remain almost constant.
  • an alternative material such as aluminum, the moment of inertia of the impeller is reduced. In practice, this means that e.g. B. with an impeller with a diameter of 670 mm, a significantly better response is achieved.
  • Figure 1 an impeller in 3D view
  • Figure 2 a sectional view of the impeller, top view
  • Figure 3 a sectional view of the impeller, side view
  • FIG. 4 an impeller with an integrated clutch
  • an impeller 1 in particular a radial fan wheel or compressor wheel.
  • This consists of a cover plate 2, a base plate 3, a hub 6 with a mounting hole 7 and blades.
  • the blades of the impeller 1 are designed as solid blades 4 and splinter blades 5.
  • the geometry of the full blades and splinter blades are identical here, since the splitter blade is part of the full blade.
  • the full blades 4 and splinter blades 5 are arranged at different angular distances and in a different order. The arrangement or sequence can be seen from the sectional view of FIG. 2.
  • the splitter vane 5.1 is followed by a full vane 4.1, then a splitter vane 5.2., Followed by four full vanes, reference numerals 4.2 to 4.5, and a splitter vane 5.3. Due to the different angular spacing and the different sequence, the noise development is further reduced while the efficiency and power consumption remain almost the same. The level and frequency of the disturbing noises, which are perceived as unpleasant, are reduced by these measures and distributed over a broader frequency band. Thanks to the constructive measures, the sound power is distributed over several individual tones, the intensity of which is correspondingly lower.
  • the impeller 1 preferably consists of an alternative material, for example aluminum. This results in a significant reduction in the moment of inertia.
  • the impeller 1 shown in FIG. 1 additionally has balancing bores 8. An unbalance of the impeller 1 is compensated for by means of these balancing bores 8. From this results a reduction in production costs, since additional balancing weights no longer have to be attached.
  • a first area 15 and a second area 16 are shown in FIG. Only full blades 4 are arranged in the first region 15. Both full and splinter blades are arranged in the second region 16.
  • the sequence of the solid blades, reference numerals 4.1 to 4.6, and the fragment blades, reference numerals 5.1 to 5.4, is irregular.
  • the angles on the air inlet side and the air outlet side between two blades are identical.
  • the angle x1 between the splitter vane 5.1 and the full vane 4.1 thus corresponds to the angle x2.
  • the angle y 1 between the full blade 4.1 and the splitter blade 5.2 corresponds to the angle y2.
  • the angles between them are different, i.e. x1 not equal to y1 and not equal to z1 applies.
  • the overall rule is that the sequence of the full blades 4 and splitter blades 5 is not rotationally symmetrical, also not in segments.
  • FIG. 3 shows a sectional view of the impeller 1 in a side view.
  • the direction of air flow is marked with arrows.
  • the air is conveyed radially outwards from the impeller 1 in the axial direction, that is to say seen from above in the drawing direction.
  • the arrangement of the full and splinter vane between the cover plate 2 and the base plate 3 can be seen from FIG.
  • FIG. 4 shows a sectional view of the impeller 1 with an integrated clutch and clutch housing 9.
  • the clutch 9 is integrated on the rear 13 in the impeller 1. This has the advantage that a higher packing density is achieved with a constant overall height of the impeller.
  • Reference number 10 denotes the connection for a housing, for example a gear housing.
  • the impeller 1 is detachably connected from the front 12 via a screw 14 to a wheel holder 11.
  • the wheel holder 1 1 is in turn firmly connected to the clutch and the clutch housing 9.
  • the impeller 1 is activated or deactivated via the state of the clutch 9. LIST OF REFERENCE NUMBERS

Abstract

The invention relates to a rotor disk (1) for an internal combustion engine, in particular a radial fan impeller or compressor disk. An uneven number of complete and solid blades (4, 5) are arranged at varying angular distances and in a varying sequence. This further reduces the generation of noise.

Description

Laufrad Wheel
Die Erfindung betrifft ein Laufrad nach dem Oberbegriff des ersten Anspruchs.The invention relates to an impeller according to the preamble of the first claim.
Bei Brennkraftmaschinen werden Laufräder beispielsweise als Radiallüfter oder alsIn internal combustion engines, for example, impellers are used as radial fans or as
Verdichterrad für einen Abgasturbolader verwendet. Problematisch bei diesen Laufrädern ist die Geräuschentwicklung, die häufig als unangenehm empfunden wird. Eine gängige Maßnahme zur Geräuschreduktion besteht darin, das Laufrad mit Voll- und Splitterschaufeln zu bestücken. Eine derartige Ausführung ist aus der EP 0 439 267 B1 bekannt. Zusätzlich kann bei diesem Laufrad die Anzahl der Vollschaufeln ungleich der Anzahl der Splitterschaufeln sein.Compressor wheel used for an exhaust gas turbocharger. The problem with these wheels is the noise, which is often perceived as unpleasant. A common measure for noise reduction is to equip the impeller with full and splinter blades. Such an embodiment is known from EP 0 439 267 B1. In addition, the number of full blades on this impeller may not be the same as the number of fragment blades.
Die der Erfindung zu Grunde liegende Aufgabe wird darin gesehen, die Geräuschemission eines Laufrades weiter zu reduzieren.The object on which the invention is based is seen in further reducing the noise emission of an impeller.
Die Aufgabe wird durch die Merkmale des ersten Anspruchs gelöst. Vorteilhafte Ausgestaltungen sind in den Unteransprüchen dargestellt.The object is achieved by the features of the first claim. Advantageous refinements are presented in the subclaims.
Vorgeschlagen wird bei einem gattungsgemäßen Laufrad, dass die Vollschaufeln und Splitterschaufeln in unterschiedlichem Winkelabstand und unterschiedlicher Reihenfolge angeordnet werden. Hierdurch wird der Störgeräusch-Pegel deutlich reduziert. Die Schallleistung verteilt sich durch die konstruktiven Maßnahmen auf mehrere Einzeltöne, deren Intensität entsprechend niedriger ausfällt. Ein weiterer Vorteil besteht darin, dass der Wirkungsgrad und die Leistungsaufnahme des Laufrades nahezu konstant bleiben. Durch die Verwendung eines alternativen Werkstoffes, beispielsweise Aluminium, wird das Massenträgheits-Moment des Laufrades abgesenkt. Für die Praxis bedeutet dies, dass z. B. bei einem Laufrad mit einem Durchmesser 670 mm, ein deutlich besseres Ansprechverhalten erzielt wird.In the case of a generic impeller, it is proposed that the solid blades and splinter blades be arranged at different angular distances and in a different order. This significantly reduces the noise level. Thanks to the constructive measures, the sound power is distributed over several individual tones, the intensity of which is correspondingly lower. Another advantage is that the efficiency and power consumption of the impeller remain almost constant. By using an alternative material, such as aluminum, the moment of inertia of the impeller is reduced. In practice, this means that e.g. B. with an impeller with a diameter of 670 mm, a significantly better response is achieved.
Durch eine entsprechende Ausformung der Rückseite des Laufrades ist es möglich, dass eine Kupplung und ein Lager integriert werden können. Hierdurch wird der Vorteil erzielt, dass bei gleichbleibender Bauhöhe die Packungsdichte vergrößert wird. Als Konsequenz ergibt sich somit eine montagefreundlichere Lösung. In den Zeichnungen ist ein bevorzugtes Ausführungsbeispiel dargestellt. Es zeigt:Appropriate shaping of the rear of the impeller makes it possible to integrate a clutch and a bearing. This has the advantage that the packing density is increased while the overall height remains the same. The consequence is a more easy-to-assemble solution. A preferred embodiment is shown in the drawings. It shows:
Figur 1 : ein Laufrad in 3D-AnsichtFigure 1: an impeller in 3D view
Figur 2: ein Schnittbild des Laufrades, DraufsichtFigure 2: a sectional view of the impeller, top view
Figur 3: ein Schnittbild des Laufrades, SeitenansichtFigure 3: a sectional view of the impeller, side view
Figur 4: ein Laufrad mit integrierter KupplungFigure 4: an impeller with an integrated clutch
In Figur 1 ist ein Laufrad 1, insbesondere Radial-Lüfterrad oder Verdichterrad, dargestellt. Dieses besteht aus einer Deckscheibe 2, einer Fußscheibe 3, einer Nabe 6 mit Befestigungsbohrung 7 und Schaufeln. Die Schaufeln des Laufrades 1 sind als Vollschaufeln 4 und Splitterschaufeln 5 ausgeführt. Die Geometrie der Vollschaufeln und Splitterschaufeln sind hierbei jedoch identisch, da die Splitterschaufel einen Teil der Vollschaufel darstellt. Die Vollschaufeln 4 und Splitterschaufeln 5 sind im unterschiedlichen Winkelabstand und unterschiedlicher Reihenfolge angeordnet. Die Anordnung bzw. Reihenfolge ist aus dem Schnittbild der Figur 2 zu ersehen. Beispielweise folgt auf die Splitterschaufel 5.1 eine Vollschaufel 4.1, dann eine Splitterschaufel 5.2., danach folgen vier Vollschaufeln, Bezugszeichen 4.2 bis 4.5, und eine Splitterschaufel 5.3. Durch den unterschiedlichen Winkelabstand und die unterschiedliche Reihenfolge wird die Geräuschentwicklung bei nahezu gleichbleibendem Wirkungsgrad bzw. Leistungsaufnahme weiter verringert. Der Pegel und die Frequenz der als unangenehm empfundenen Störgeräusche werden durch diese Maßnahmen abgesenkt und auf ein breiteres Frequenzband verteilt. Die Schallleistung verteilt sich durch die konstruktiven Maßnahmen auf mehrere Einzeltöne, deren Intensität entsprechend niedriger ausfällt.1 shows an impeller 1, in particular a radial fan wheel or compressor wheel. This consists of a cover plate 2, a base plate 3, a hub 6 with a mounting hole 7 and blades. The blades of the impeller 1 are designed as solid blades 4 and splinter blades 5. However, the geometry of the full blades and splinter blades are identical here, since the splitter blade is part of the full blade. The full blades 4 and splinter blades 5 are arranged at different angular distances and in a different order. The arrangement or sequence can be seen from the sectional view of FIG. 2. For example, the splitter vane 5.1 is followed by a full vane 4.1, then a splitter vane 5.2., Followed by four full vanes, reference numerals 4.2 to 4.5, and a splitter vane 5.3. Due to the different angular spacing and the different sequence, the noise development is further reduced while the efficiency and power consumption remain almost the same. The level and frequency of the disturbing noises, which are perceived as unpleasant, are reduced by these measures and distributed over a broader frequency band. Thanks to the constructive measures, the sound power is distributed over several individual tones, the intensity of which is correspondingly lower.
Vorzugsweise besteht das Laufrad 1 aus einem alternativen Werkstoff, beispielsweise Aluminium. Dies ergibt eine deutliche Verringerung des Massenträgheits-Moments.The impeller 1 preferably consists of an alternative material, for example aluminum. This results in a significant reduction in the moment of inertia.
Das in Figur 1 dargestellte Laufrad 1 weist zusätzlich Wuchtbohrungen 8 auf. Mittels dieser Wuchtbohrungen 8 wird eine Unwucht des Laufrades 1 ausgeglichen. Hieraus ergibt sich eine Kostenreduktion bei der Herstellung, da zusätzliche Wucht-Gewichte nicht mehr angebracht werden müssen.The impeller 1 shown in FIG. 1 additionally has balancing bores 8. An unbalance of the impeller 1 is compensated for by means of these balancing bores 8. From this results a reduction in production costs, since additional balancing weights no longer have to be attached.
In der Figur 2 ist ein erster Bereich 15 und ein zweiter Bereich 16 eingezeichnet. Im ersten Bereich 15 sind ausschließlich Vollschaufeln 4 angeordnet. Im zweiten Bereich 16 sind sowohl Voll- als auch Splitterschaufeln angeordnet. Im zweiten Bereich 16 ist die Reihenfolge der Vollschaufeln, Bezugszeichen 4.1 bis 4.6, und der Splitterschaufeln, Bezugszeichen 5.1 bis 5.4, unregelmäßig. Die Winkel auf der Luft-Eintrittsseite und der Luft-Austrittsseite zwischen zwei Schaufeln sind identisch. Der Winkel x1 zwischen der Splitterschaufel 5.1 und der Vollschaufel 4.1 entspricht also dem Winkel x2. Der Winkel y 1 zwischen der Vollschaufel 4.1 und der Splitterschaufel 5.2 entspricht dem Winkel y2. Gleiches gilt für den Winkel z1 und z2. Die Winkel untereinander sind jedoch unterschiedlich, das heißt, es gilt x1 ungleich y1 und ungleich z1. Für das Laufrad 1 gilt insgesamt, dass die Reihenfolge der Vollschaufeln 4 und Splitterschaufeln 5 nicht rotationssymmetrisch, auch nicht segmentweise, ist.A first area 15 and a second area 16 are shown in FIG. Only full blades 4 are arranged in the first region 15. Both full and splinter blades are arranged in the second region 16. In the second area 16, the sequence of the solid blades, reference numerals 4.1 to 4.6, and the fragment blades, reference numerals 5.1 to 5.4, is irregular. The angles on the air inlet side and the air outlet side between two blades are identical. The angle x1 between the splitter vane 5.1 and the full vane 4.1 thus corresponds to the angle x2. The angle y 1 between the full blade 4.1 and the splitter blade 5.2 corresponds to the angle y2. The same applies to the angles z1 and z2. However, the angles between them are different, i.e. x1 not equal to y1 and not equal to z1 applies. For the impeller 1, the overall rule is that the sequence of the full blades 4 and splitter blades 5 is not rotationally symmetrical, also not in segments.
In Figur 3 ist ein Schnittbild des Laufrades 1 in Seitenansicht dargestellt. Die Strömungsrichtung der Luft ist mit Pfeilen gekennzeichnet. Wie dargestellt wird die Luft in axialer Richtung, also in Zeichnungsrichtung gesehen von oben, vom Laufrad 1 radial nach außen gefördert. Daneben ist aus der Figur 3 die Anordnung der Voll- und Splitterschaufel zwischen der Deckscheibe 2 und der Fußscheibe 3 ersichtlich.3 shows a sectional view of the impeller 1 in a side view. The direction of air flow is marked with arrows. As shown, the air is conveyed radially outwards from the impeller 1 in the axial direction, that is to say seen from above in the drawing direction. In addition, the arrangement of the full and splinter vane between the cover plate 2 and the base plate 3 can be seen from FIG.
In Figur 4 ist ein Schnittbild des Laufrades 1 mit integrierter Kupplung und Kupplungsgehäuse 9 dargestellt. Die Kupplung 9 ist auf der Rückseite 13 im Laufrad 1 integriert. Hierdurch wird der Vorteil erzielt, dass bei gleichbleibender Bauhöhe des Laufrades eine höhere Packungsdichte verwirklicht wird. Mit Bezugszeichen 10 ist der Anschluss für ein Gehäuse, beispielsweise ein Getriebe-Gehäuse, bezeichnet. Das Laufrad 1 wird von der Vorderseite 12 über eine Schraube 14 mit einer Radaufnahme 1 1 lösbar verbunden. Die Radaufnahme 1 1 wiederum ist mit der Kupplung und dem Kupplungs- Gehäuse 9 fest verbunden. Über den Zustand der Kupplung 9 wird das Laufrad 1 aktiviert bzw. deaktiviert. BezugszeichenlisteFIG. 4 shows a sectional view of the impeller 1 with an integrated clutch and clutch housing 9. The clutch 9 is integrated on the rear 13 in the impeller 1. This has the advantage that a higher packing density is achieved with a constant overall height of the impeller. Reference number 10 denotes the connection for a housing, for example a gear housing. The impeller 1 is detachably connected from the front 12 via a screw 14 to a wheel holder 11. The wheel holder 1 1 is in turn firmly connected to the clutch and the clutch housing 9. The impeller 1 is activated or deactivated via the state of the clutch 9. LIST OF REFERENCE NUMBERS
LaufradWheel
Deckscheibecover disc
Fußscheibebasal disc
Vollschaufelfull blade
Splitterschaufelsplitter blade
Nabehub
Befestigungsbohrungmounting hole
Wuchtbohrungbalancing hole
Kupplung mit Kupplungs-GehäuseCoupling with coupling housing
Anschlussconnection
Radaufnahmewheel
Vorderseitefront
Rückseiteback
Schraube erster Bereich zweiter Bereich Screw first area second area

Claims

PATENTANSPRÜCHE
1. Laufrad, insbesondere Radial-Lüfterrad oder Verdichterrad, welches eine ungleiche Anzahl von Voll- und Splitterschaufeln aufweist, dadurch gekennzeichnet, dass die Vollschaufeln (4) und Splitterschaufeln (5) in unterschiedlichem Winkelabstand und unterschiedlicher Reihenfolge angeordnet werden.1. impeller, in particular radial fan wheel or compressor wheel, which has an unequal number of full and splitter blades, characterized in that the full blades (4) and splitter blades (5) are arranged at different angular intervals and in a different order.
2. Laufrad (1) nach Anspruch 1, dadurch gekennzeichnet, dass auf einer Rückseite (13) des Laufrads (1) eine Kupplung (9) und Lager integriert werden.2. impeller (1) according to claim 1, characterized in that on a rear side (13) of the impeller (1) a clutch (9) and bearings are integrated.
3. Laufrad (1) nach Anspruch 2, dadurch gekennzeichnet, dass das Laufrad (1) aus einem alternativen Werkstoff hergestellt wird.3. impeller (1) according to claim 2, characterized in that the impeller (1) is made of an alternative material.
4. Laufrad (1) nach Anspruch 3, dadurch gekennzeichnet, dass auf dem Laufrad (1) Wuchtbohrungen (8) angeordnet werden mittels denen eine Unwucht des4. impeller (1) according to claim 3, characterized in that on the impeller (1) balancing bores (8) are arranged by means of which an unbalance of the
Lüfterrades (1) ausgeglichen wird.Fan wheel (1) is compensated.
5. Laufrad (1) nach Anspruch 4, dadurch gekennzeichnet, dass die Wuchtbohrungen (8) auf einer Deckscheibe (2) und/oder Fußscheibe (3) angeordnet werden. 5. impeller (1) according to claim 4, characterized in that the balancing holes (8) on a cover plate (2) and / or base plate (3) are arranged.
PCT/EP2002/004920 2001-05-09 2002-05-04 Rotor disk WO2002090776A2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/476,990 US20040202539A1 (en) 2001-05-09 2002-05-04 Rotor disk
EP02769136A EP1387962A2 (en) 2001-05-09 2002-05-04 Rotor disk

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10122516A DE10122516B4 (en) 2001-05-09 2001-05-09 Wheel
DE10122516.4 2001-05-09

Publications (2)

Publication Number Publication Date
WO2002090776A2 true WO2002090776A2 (en) 2002-11-14
WO2002090776A3 WO2002090776A3 (en) 2003-02-27

Family

ID=7684151

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2002/004920 WO2002090776A2 (en) 2001-05-09 2002-05-04 Rotor disk

Country Status (4)

Country Link
US (1) US20040202539A1 (en)
EP (1) EP1387962A2 (en)
DE (1) DE10122516B4 (en)
WO (1) WO2002090776A2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007009366A1 (en) * 2007-02-23 2008-08-28 Sew-Eurodrive Gmbh & Co. Kg Fan wheel, system and transmission series
DE102008010912A1 (en) 2007-02-23 2008-08-28 Sew-Eurodrive Gmbh & Co. Kg Fan wheel, system and transmission series
WO2009027260A1 (en) * 2007-08-30 2009-03-05 Siemens Aktiengesellschaft Radial compressor wheel

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202005015357U1 (en) 2004-10-09 2006-01-05 Ebm-Papst St. Georgen Gmbh & Co. Kg Fan with a fan
US8007241B2 (en) * 2007-11-27 2011-08-30 Nidec Motor Corporation Bi-directional cooling fan
CZ304593B6 (en) * 2008-10-29 2014-07-23 Vysoké Učení Technické V Brně Hydraulic machine impeller wheel
DE102009007843A1 (en) 2009-02-06 2010-08-12 Bosch Mahle Turbo Systems Gmbh & Co. Kg Compressor wheel for exhaust gas turbocharger, has split blades arranged between two consecutive complete blades, where blade periods comprise four blades such as one complete blade and three split blades
DE102010039219A1 (en) * 2010-08-11 2012-02-16 Behr Gmbh & Co. Kg Fan i.e. engine cooling fan, for use as axial blower to cool combustion engine of motor car, has fan wheel comprising fan blades, which are enclosed by fan cladding, and secondary fan inhibiting back flow of air promoted by fan wheel
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DE102015112732A1 (en) * 2015-08-03 2017-02-09 Ebm-Papst St. Georgen Gmbh & Co. Kg Method for balancing a fan device and fan device, which is balanced by a method
DE102015112731A1 (en) * 2015-08-03 2017-02-09 Ebm-Papst St. Georgen Gmbh & Co. Kg Fan device and method for balancing a fan device
DE102017100800A1 (en) 2017-01-17 2018-07-19 Eberspächer Climate Control Systems GmbH & Co. KG Heizluftförderrad
CN206617363U (en) * 2017-03-01 2017-11-07 讯凯国际股份有限公司 Impeller
CN107448415A (en) * 2017-08-23 2017-12-08 联想(北京)有限公司 A kind of electronic equipment and its radiator fan
US11105203B2 (en) 2018-01-29 2021-08-31 Carrier Corporation High efficiency centrifugal impeller with balancing weights
CN112460065B (en) * 2019-09-06 2022-08-30 台达电子工业股份有限公司 Impeller and fan thereof
JP2022046381A (en) * 2020-09-10 2022-03-23 三菱重工エンジン＆ターボチャージャ株式会社 Turbine wheel, turbine and turbocharger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174855C (en) * 1905-08-19 1906-10-01 Wittig Emil IMPELLER FOR FANS
US912362A (en) * 1907-04-23 1909-02-16 George Marie Capell Centrifugal fan and pump.
GB1293553A (en) * 1969-02-18 1972-10-18 Cav Ltd Radial flow fans
GB2046360A (en) * 1979-03-31 1980-11-12 Aes Plastics Ltd Fluid impeller
EP0439267A1 (en) * 1990-01-26 1991-07-31 Schwitzer U.S. Inc. Compressor impeller with displaced splitter blades
EP0516073A1 (en) * 1991-05-29 1992-12-02 Alcatel SEL Aktiengesellschaft Apparatus for transporting a gaseous medium

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2658455A (en) * 1948-02-26 1953-11-10 Laval Steam Turbine Co Impeller with center intake
US2781963A (en) * 1950-06-16 1957-02-19 Guy S Faber Blower
DE1707136U (en) * 1955-05-20 1955-09-15 Gerhard Dr Ing Schemberger IMPELLER FOR CENTRIFUGAL FAN.
US3387768A (en) * 1966-04-08 1968-06-11 Rotron Mfg Co Fastener
US3627445A (en) * 1968-04-17 1971-12-14 S E R M A G Soc D Etudes Et De Ventilating device for cooling a heat engine
US3622249A (en) * 1968-08-18 1971-11-23 Aisin Seiki Fan assembly
JPS5525555A (en) * 1978-08-12 1980-02-23 Hitachi Ltd Impeller
US4257744A (en) * 1979-03-21 1981-03-24 Westinghouse Electric Corp. Impeller and shaft assembly for high speed gas compressor
DE9102865U1 (en) * 1991-03-09 1992-07-16 Robert Bosch Gmbh, 7000 Stuttgart, De
US5158435A (en) * 1991-11-15 1992-10-27 Praxair Technology, Inc. Impeller stress improvement through overspeed
DE4445671B4 (en) * 1994-12-21 2005-03-24 Behr Gmbh & Co. Kg Axial fan for a radiator of a motor vehicle engine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174855C (en) * 1905-08-19 1906-10-01 Wittig Emil IMPELLER FOR FANS
US912362A (en) * 1907-04-23 1909-02-16 George Marie Capell Centrifugal fan and pump.
GB1293553A (en) * 1969-02-18 1972-10-18 Cav Ltd Radial flow fans
GB2046360A (en) * 1979-03-31 1980-11-12 Aes Plastics Ltd Fluid impeller
EP0439267A1 (en) * 1990-01-26 1991-07-31 Schwitzer U.S. Inc. Compressor impeller with displaced splitter blades
EP0516073A1 (en) * 1991-05-29 1992-12-02 Alcatel SEL Aktiengesellschaft Apparatus for transporting a gaseous medium

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HANSEN B: "ASYMMETRIC COOLING FAN QUIETENS INDUSTRIAL MOTORS" EUREKA (INC. ENGINEERING MATERIALS AND DESIGN), FINDLAY PUBLICATIONS, HORTON KIRBY, KENT, GB, Bd. 14, Nr. 3, 1. März 1994 (1994-03-01), Seite 7 XP000433003 ISSN: 0261-2097 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007009366A1 (en) * 2007-02-23 2008-08-28 Sew-Eurodrive Gmbh & Co. Kg Fan wheel, system and transmission series
DE102008010912A1 (en) 2007-02-23 2008-08-28 Sew-Eurodrive Gmbh & Co. Kg Fan wheel, system and transmission series
DE102007009366B4 (en) * 2007-02-23 2017-06-14 Sew-Eurodrive Gmbh & Co Kg Fan wheel, system and transmission series
DE102008010912B4 (en) * 2007-02-23 2020-11-12 Sew-Eurodrive Gmbh & Co Kg Fan wheel, system and gear series
WO2009027260A1 (en) * 2007-08-30 2009-03-05 Siemens Aktiengesellschaft Radial compressor wheel

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US20040202539A1 (en) 2004-10-14
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DE10122516A1 (en) 2002-11-28

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