EP3571416B1 - Shrouded centrifugal fan impeller with a periodically and asymmetrically shaped shroud - Google Patents
Shrouded centrifugal fan impeller with a periodically and asymmetrically shaped shroud Download PDFInfo
- Publication number
- EP3571416B1 EP3571416B1 EP18762797.1A EP18762797A EP3571416B1 EP 3571416 B1 EP3571416 B1 EP 3571416B1 EP 18762797 A EP18762797 A EP 18762797A EP 3571416 B1 EP3571416 B1 EP 3571416B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fan wheel
- blade
- radial
- axial width
- blades
- 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.)
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- 238000010586 diagram Methods 0.000 description 4
- 238000000926 separation method Methods 0.000 description 3
- 230000008092 positive effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- 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
- F04D29/02—Selection of particular materials
- F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
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- 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
- F05D2250/00—Geometry
- F05D2250/70—Shape
Definitions
- the invention relates to a radial fan wheel with a plurality of fan wheel blades arranged in a blade ring and at least one disc which covers the fan wheel blades axially at least in sections on the front side.
- Radial fan wheels are known from the prior art in various designs and are used in a variety of blowers with different purposes. It is also known that flow separations should be avoided as much as possible, as these reduce the efficiency of the blowers or fans and lead to increased noise. Typically, the suction side of the impeller blades tends to cause flow separation during operation due to boundary layer overloading, while the flow is on the pressure side of the impeller blades.
- the invention is therefore based on the object of providing a fan wheel which leads to increased efficiency and improved noise behavior in radial blowers.
- a radial impeller according to claim 1 is proposed.
- the radial fan wheel has a plurality of fan wheel blades arranged in a blade ring and at least one disk which covers the fan wheel blades axially on the front side at least in sections, with two adjacent fan wheel blades each forming a blade channel between them, the flow cross section of which is limited axially by the disk.
- the axial width of the blade channel increases at least along an outer circumference of the radial fan wheel, starting from a suction side of a fan wheel blade delimiting the blade channel towards a pressure side of the adjacent fan wheel blade delimiting the blade channel, up to a maximum.
- the maximum lies on a radial section of the fan wheel, which lies between 65 - 80% of the distance between the suction side of the fan wheel blade delimiting the blade channel and the pressure side of the adjacent fan wheel blade delimiting the blade channel, so that the disk, viewed in the circumferential direction, is asymmetrical between two adjacent fan wheel blades has shape.
- the asymmetrical design of the disk of the radial fan wheel according to the invention leads to a narrowing of the blade channel in the area of the suction side of the fan wheel blade and to an enlargement of the blade channel or its flow cross-sectional area in the area of the pressure side of the fan wheel blade. This stabilizes the flow in the area of the suction side and prevents or minimizes flow separation.
- the increase in the flow cross-section takes place in particular without abruptly changing the course of the flow cross-section and therefore advantageously through a constant course of the disk in the circumferential direction.
- the disk between all adjacent fan wheel blades is of identical shape, so that the flow channels running between the fan wheel blades are also each of the same shape.
- an embodiment of the radial impeller is favorable in which the impeller blades have a constant axial width, in particular at the outer radius of the radial impeller.
- the entire fan wheel blades of the blade ring are designed to have identical shapes in an advantageous solution.
- b x B.S + BE ⁇ BE P ⁇ X / P 2 with X ⁇ P
- b x B.S + BE ⁇ BE X ⁇ P / 1 ⁇ P 2 with X > P , as well as 0 ⁇ P ⁇ 1 , certainly.
- BS corresponds to an axial width of the blade channel on the impeller blade, BE to the expansion of the axial width of the blade channel up to the maximum, P to a position of the maximum of the axial width of the blade channel starting from the suction side of the impeller blade delimiting the blade channel and X to a circumferential direction of a developed cut along the Disc contour, ie a course along the outer contour of the radial fan wheel.
- the axial width of the respective blade channel increases to the maximum at position P and then decreases again.
- the formulas express the course of the axial width of the blade channel in the circumferential direction between two adjacent impeller blades. On the adjacent impeller blades, the value of the axial width corresponds to BS. In the area in between, the axial width of the blade channel increases by the extension BE with the off-center maximum of the axial width B.
- an advantageous embodiment provides that the disk is formed by the suction-side cover disk.
- the invention is not limited to this, so that the disk can also be realized by the base disk, which usually also forms at least parts of the hub of the radial fan wheel.
- the increase in the axial width of the flow cross section of the flow channel is formed by both the base and the cover plate with a correspondingly asymmetrical contour on both sides is.
- the fan wheel blades are preferably curved in the circumferential direction and are flush with the outer edge of the base disk and/or cover disk.
- FIGS. 1 and 2 show an exemplary embodiment of a radial fan wheel 1 with a plurality of backwardly curved blades arranged in a blade ring Impeller blades 4, the lower axial end faces of which are completely covered by the bottom disk 3, which extends parallel to the axial plane running perpendicular to the axis of rotation of the radial impeller 1.
- the fan wheel blades 4 are partially covered with the suction-side cover plate 2, the fan wheel blades 4 being exposed in the area of the suction opening 7 of the radial fan wheel 1 and extending with an arcuate radial end edge in the direction of the base plate 3.
- the suction opening 7 is formed by the circular peripheral edge 9.
- Two adjacent fan blades 4 each form a blade channel 5 between them, the flow cross sections of which are determined and limited by the fan blades 4, the flat base disk 3 and the cover disk 2.
- all impeller blades 4 are identical and have a constant axial width.
- All flow channels 5 also have the identical shape, since the cover plate 2 between all adjacent fan wheel blades 4 is also designed to have the same shape.
- the axial width B of the respective blade channel 5 is not constant over the extent in the circumferential direction of the radial fan wheel 1, but is adjusted via the shape of the cover disk, so that it extends from the suction side S of the fan wheel blade 4 in the direction of the pressure side D of the adjacent fan wheel blade 4 an axial width of the fan wheel blade BS increases to the maximum M and then reduces back to the size of the axial width BS of the adjacent fan wheel blade 4.
- the course of the cover plate 2 is continuous.
- the maximum is off-center and on a radial section of the radial fan wheel 1, which in the embodiment shown is at 75% of the distance between the suction side S of the fan wheel blade 4 and the pressure side D of the adjacent fan wheel blade 4, measured at the outer radius of the radial fan wheel 1, so that the Cover plate 2 seen in the circumferential direction between two adjacent ones Fan wheel blades 4 have an asymmetrical shape.
- the asymmetrical shape is determined in particular on the outer radius of the radial fan wheel 1, but also runs radially inwards over a certain length, so that a three-dimensional axial width increase is present in the radial outer area of the pressure side D of the individual fan wheel blades 4.
- the asymmetrical shape of the cover plate 2 continuously changes into a symmetrical shape in the direction pointing radially inwards towards the suction opening 7, with the collar 8 adjacent to the suction opening already being designed as a ring.
- FIG 3 is a diagram of the course of the axial width B of the blade channel 5 along the circumferential direction X of the radial fan wheel 1 Fig. 1 at its outer radius and therefore the ratio of the flow cross-sectional area of one of the flow channels 5 at the flow channel outlet.
- the center Z of the blade channel 5 between two adjacent impeller blades 4 is represented by the dot-dash line, with the suction side S lying to the left of the center Z and the pressure side of the impeller blades 4 to the right of the center Z.
- the mean axial width MB is shown as a dashed line.
- the maximum M of the axial width B is entered as a dotted line at 75% of the distance between the suction side S of the impeller blade 4 and the pressure side D of the adjacent impeller blade 4.
- FIG 4 is a diagram with characteristic curves measured with an identical test setup for the pressure curve psf [Pa] and the efficiency nse [%] at different volume flows qv [m 3 /h] of the radial fan wheel 1 Fig. 1 and the identical radial fan wheel 100 only with a flat cover plate 200 Figure 5 shown, with the solid characteristics showing the radial fan wheel 1 according to Figure 1 with the cover plate 2 and the fine-dotted characteristic curves each correspond to the radial fan wheel 100 Figure 5 mark.
- the advantageous effect with increased peak efficiency starts with a volume flow of approx. 150 m 3 /h and upwards.
- the superior pressure curve starts at approx. 225 m 3 /h.
- the reduction in noise generation is at least 5% in the range from 225 m 3 /h.
Description
Die Erfindung betrifft ein Radialgebläserad mit einer Vielzahl von in einem Schaufelkranz angeordneten Gebläseradschaufeln sowie zumindest einer die Gebläseradschaufeln axial stirnseitig zumindest abschnittsweise überdeckenden Scheibe.The invention relates to a radial fan wheel with a plurality of fan wheel blades arranged in a blade ring and at least one disc which covers the fan wheel blades axially at least in sections on the front side.
Radialgebläseräder sind aus dem Stand der Technik in verschiedenen Ausführungen bekannt und werden in einer Vielzahl von Gebläsen mit unterschiedlichen Einsatzzwecken eingesetzt. Dabei ist auch bekannt, dass Strömungsablösungen so weit als möglich zu vermeiden sind, da diese die Effizienz der Gebläse bzw. Ventilatoren reduzieren und zu einer erhöhten Geräuschbildung führen. Typischerweise neigt die Saugseite der Gebläseradschaufeln im Betrieb zu Strömungsablösungen durch Grenzschichtüberlastung, während die Strömung an der Druckseite der Gebläseradschaufeln anliegt.Radial fan wheels are known from the prior art in various designs and are used in a variety of blowers with different purposes. It is also known that flow separations should be avoided as much as possible, as these reduce the efficiency of the blowers or fans and lead to increased noise. Typically, the suction side of the impeller blades tends to cause flow separation during operation due to boundary layer overloading, while the flow is on the pressure side of the impeller blades.
Zur Erhöhung der Effizienz wurden bereits früher Anstrengungen unternommen, beispielsweise durch Gebläseräder wie sie die
Weiter ist beispielsweise aus dem Dokument
Der Erfindung liegt deshalb die Aufgabe zugrunde, ein Gebläserad bereit zu stellen, das bei Radialgebläsen zu einer erhöhten Effizienz und verbessertem Geräuschverhalten führt.The invention is therefore based on the object of providing a fan wheel which leads to increased efficiency and improved noise behavior in radial blowers.
Diese Aufgabe wird durch die Merkmalskombination gemäß Anspruch 1 gelöst.This task is solved by the combination of features according to
Erfindungsgemäß wird ein Radialgebläserad gemäß Anspruch 1 vorgeschlagen. Das Radialgebläserad weist eine Vielzahl von in einem Schaufelkranz angeordneten Gebläseradschaufeln sowie zumindest eine die Gebläseradschaufeln axial stirnseitig zumindest abschnittsweise überdeckenden Scheibe auf, wobei zwei benachbarte Gebläseradschaufeln zwischen sich jeweils einen Schaufelkanal bilden, dessen Durchströmungsquerschnitt axial durch die Scheibe begrenzt wird. Die Axialbreite des Schaufelkanals vergrößert sich dabei zumindest entlang eines Außenumfangs des Radialgebläserads ausgehend von einer Saugseite einer den Schaufelkanal begrenzenden Gebläseradschaufel in Richtung einer Druckseite der benachbarten, den Schaufelkanal begrenzenden Gebläseradschaufel bis auf ein Maximum. Zudem liegt das Maximum auf einem Radialschnitt des Gebläserads, der zwischen 65 - 80% des Abstands zwischen der Saugseite der den Schaufelkanal begrenzenden Gebläseradschaufel und der Druckseite der benachbarten, den Schaufelkanal begrenzenden Gebläseradschaufel liegt, so dass die Scheibe in Umfangsrichtung gesehen zwischen zwei benachbarten Gebläseradschaufein eine asymmetrische Form aufweist.According to the invention, a radial impeller according to
Die erfindungsgemäße asymmetrische Gestaltung der Scheibe des Radialgebläserads führt zu einer Verengung des Schaufelkanals im Bereich der Saugseite der Gebläseradschaufel und zu einer Vergrößerung des Schaufelkanals bzw. seiner Durchströmungsquerschnittsfläche im Bereich der Druckseite der Gebläseradschaufel. Dadurch wird die Strömung im Bereich der Saugseite stabilisiert und eine Strömungsablösung verhindert bzw. minimiert.The asymmetrical design of the disk of the radial fan wheel according to the invention leads to a narrowing of the blade channel in the area of the suction side of the fan wheel blade and to an enlargement of the blade channel or its flow cross-sectional area in the area of the pressure side of the fan wheel blade. This stabilizes the flow in the area of the suction side and prevents or minimizes flow separation.
Die Vergrößerung des Durchströmungsquerschnitts erfolgt insbesondere ohne den Verlauf des Durchströmungsquerschnitts sprunghaft zu ändern und mithin vorteilhafterweise durch einen stetigen Verlauf der Scheibe in Umfangsrichtung.The increase in the flow cross-section takes place in particular without abruptly changing the course of the flow cross-section and therefore advantageously through a constant course of the disk in the circumferential direction.
Als übliche und vorteilhafte Ausführung wird bei dem Radialgebläserad vorgesehen, dass die Scheibe zwischen allen jeweils benachbarten Gebläseradschaufeln formidentisch ausgebildet ist, so dass auch die zwischen den Gebläseradschaufeln verlaufenden Strömungskanäle jeweils formgleich sind.As a usual and advantageous embodiment, it is provided for the radial fan wheel that the disk between all adjacent fan wheel blades is of identical shape, so that the flow channels running between the fan wheel blades are also each of the same shape.
Ferner ist eine Ausführung des Radialgebläserads günstig, bei der die Gebläseradschaufeln eine konstante Axialbreite aufweisen, insbesondere am Außenradius des Radialgebläserads. Zudem werden die gesamten Gebläseradschaufeln des Schaufelkranzes in einer vorteilhaften Lösung formidentisch ausgebildet.Furthermore, an embodiment of the radial impeller is favorable in which the impeller blades have a constant axial width, in particular at the outer radius of the radial impeller. In addition, the entire fan wheel blades of the blade ring are designed to have identical shapes in an advantageous solution.
Die Axialbreite des jeweiligen Schaufelkanals entlang des Außenumfangs des erfindungsgemäßen Radialgebläserads ist durch die Formeln
Da sich die Strömung an der Saugseite der Gebläseradschaufeln typischerweise an der Deckscheibe ablöst, ist die positive Wirkung der asymmetrischen Vergrößerung der Axialbreite des Durchströmungsquerschnitts des Strömungskanals auf den Wirkungsgrad an der ansaugseiteigen Deckscheibe höher. Deshalb sieht eine vorteilhafte Ausführung vor, dass die Scheibe durch die ansaugseitige Deckscheibe gebildet wird. Die Erfindung ist jedoch nicht hierauf beschränkt, so dass die Scheibe auch durch die Bodenscheibe, welche zumeist auch zumindest Teile der Nabe des Radialgebläserads bildet, realisiert werden kann. Schließlich ist auch eine Ausführungsvariante umfasst, bei der die Vergrößerung der Axialbreite des Durchströmungsquerschnitts des Strömungskanals durch sowohl die Boden- als auch die Deckscheibe mit einer entsprechend beidseitig asymmetrischen Kontur gebildet ist.Since the flow on the suction side of the impeller blades typically separates from the cover plate, the positive effect of the asymmetrical increase in the axial width of the flow cross section of the flow channel on the efficiency on the suction side cover plate is higher. Therefore, an advantageous embodiment provides that the disk is formed by the suction-side cover disk. However, the invention is not limited to this, so that the disk can also be realized by the base disk, which usually also forms at least parts of the hub of the radial fan wheel. Finally, an embodiment variant is also included in which the increase in the axial width of the flow cross section of the flow channel is formed by both the base and the cover plate with a correspondingly asymmetrical contour on both sides is.
Die Gebläseradschaufeln verlaufen vorzugsweise in Umfangsrichtung gekrümmt und schließen bündig mit dem Außenrand der Bodenscheibe und/oder Deckscheibe ab.The fan wheel blades are preferably curved in the circumferential direction and are flush with the outer edge of the base disk and/or cover disk.
Andere vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet bzw. werden nachstehend zusammen mit der Beschreibung der bevorzugten Ausführung der Erfindung anhand der Figuren näher dargestellt. Es zeigen:
- Fig. 1
- ein Ausführungsbeispiel eines Radialgebläserads in einer perspektivischen Ansicht;
- Fig. 2
- das Ausführungsbeispiel des Radialgebläserads aus
Fig. 1 in einer seitlichen Ansicht; - Fig. 3
- ein Diagramm zum Verlauf der Axialbreite eines Schaufelkanals entlang der Umfangsrichtung des Radialgebläserads;
- Fig. 4
- ein Diagramm zum Vergleich des Wirkungsgrads und des Druckverlaufs des Radialgebläserads aus
Fig. 1 gegenüber einem Radialgebläserads gemäß dem Stand der Technik ausFig. 5 ; - Fig. 5
- ein Radialgebläserad gemäß dem Stand der Technik.
- Fig. 1
- an embodiment of a radial impeller in a perspective view;
- Fig. 2
- the exemplary embodiment of the radial impeller
Fig. 1 in a side view; - Fig. 3
- a diagram showing the course of the axial width of a blade channel along the circumferential direction of the radial impeller;
- Fig. 4
- a diagram to compare the efficiency and the pressure curve of the radial impeller
Fig. 1 compared to a radial fan wheel according to the prior artFig. 5 ; - Fig. 5
- a radial fan wheel according to the prior art.
Gleiche Bezugszeichen benennen gleiche Teile bzw. Elemente in allen Figu- ren.The same reference numbers designate the same parts or elements in all figures.
Die
Die Axialbreite B des jeweiligen Schaufelkanals 5 ist über die Erstreckung in Umfangsrichtung des Radialgebläserads 1 nicht konstant, sondern wird über die Form der Deckscheibe angepasst, so dass sie sich ausgehend von der Saugseite S der Gebläseradschaufel 4 in Richtung der Druckseite D der benachbarten Gebläseradschaufel 4 von einer Axialbreite der Gebläseradschaufel BS bis auf das Maximum M vergrößert und sich anschließend zurück auf die Größe der Axialbreite BS der benachbarten Gebläseradschaufel 4 verringert. Der Verlauf der Deckscheibe 2 ist dabei stetig. Das Maximum liegt außermittig und auf einem Radialschnitt des Radialgebläserads 1, der in der gezeigten Ausführung bei 75% des Abstands zwischen der Saugseite S der Gebläseradschaufel 4 und der Druckseite D der benachbarten Gebläseradschaufel 4, gemessen am Außenradius des Radialgebläserads 1, liegt, so dass die Deckscheibe 2 in Umfangsrichtung gesehen zwischen zwei benachbarten Gebläseradschaufeln 4 eine asymmetrische Form aufweist. Die asymmetrische Form ist insbesondere am Außenradius des Radialgebläserads 1 bestimmt, verläuft aber zudem über eine bestimmte Länge auch radial einwärts, so dass eine dreidimensionale Axialbreitenvergrößerung im radialen Außenbereich der Druckseite D der einzelnen Gebläseradschaufeln 4 vorliegt. Die asymmetrische Form der Deckscheibe 2 geht stetig in der nach radial innen zur Ansaugöffnung 7 weisenden Richtung in eine symmetrische Form über, wobei der an die Ansaugöffnung angrenzende Bund 8 bereits als Ring ausgebildet ist.The axial width B of the
In
In
In eine Ausführung gemäß
Claims (7)
- A radial fan wheel (1) having a plurality of fan wheel blades (4) arranged in a blade ring and at least one plate that, at least in sections, covers the fan wheel blades (4) axially on the front side, wherein two adjacent fan wheel blades (4) form a blade channel (5) therebetween, the flow cross section of which is axially limited by the plate, an axial width of the blade channel increasing to a maximum (M) at least along an outer periphery of the radial fan wheel (1) starting from a suction side (S) of a fan wheel blade (4) limiting the blade channel (5) in the direction of a pressure side (D) of the adjacent fan wheel blade limiting the blade channel (5), wherein the maximum lies on a radial section of the fan wheel, which radial section lies between 55 and 95% of the distance between the suction side (S) of the fan wheel blade limiting the blade channel (5) and the pressure side (D) of the adjacent fan wheel blade (4) limiting the blade channel (5) such that the plate, when viewed in the circumferential direction, has an asymmetrical shape between two adjacent fan wheel blades (4), characterized in thatthe maximum (M) lies on a radial section of the radial fan wheel (1), which radial section lies between 65 and 80% of the distance between the suction side (S) of the fan wheel blade (4) limiting the blade channel (5) and the pressure side (D) of the adjacent fan wheel blade (4) limiting the blade channel (5), whereinthe axial width (B) of each blade channel (5) along the outer periphery of the radial fan wheel (1) is defined by the formulaswherein BS is an axial width of the blade channel (5) at the fan wheel blade (4), BE is the extension of the axial width of the blade channel to the maximum, P is a position of the maximum (M) of the axial width of the blade channel (5) starting from the suction side (S) of the fan wheel blade (4) limiting the blade channel (5) and X is a circumferential direction of an unfolded section along the contour of the plate.
- The radial fan wheel according to claim 1, characterized in that the plate has a continuous curvature in the circumferential direction.
- The radial fan wheel according to one of the preceding claims, characterized in that the fan wheel blades (4) have a constant axial width (B).
- The radial fan wheel according to one of the preceding claims, characterized in that the adjacent fan wheel blades (4) have an identical axial width (B) at the outer radius of the radial fan wheel (1).
- The radial fan wheel according to one of the preceding claims, characterized in that the fan wheel blades (4) of the blade ring are formed identical in shape and have an identical axial width (B) at the outer radius of the radial fan wheel (1).
- The radial fan wheel according to one of the preceding claims, characterized in that the plate is formed identical in shape between all adjacent fan wheel blades (4).
- The radial fan wheel according to one of the preceding claims, characterized in that the plate is provided by a bottom plate (3) and/or a suction side cover plate (2).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017120537.3A DE102017120537A1 (en) | 2017-09-06 | 2017-09-06 | Radial blower wheel with asymmetrical disc |
PCT/EP2018/072693 WO2019048241A1 (en) | 2017-09-06 | 2018-08-22 | Covered radial fan wheel with a periodically and asymmetrically shaped plate |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3571416A1 EP3571416A1 (en) | 2019-11-27 |
EP3571416B1 true EP3571416B1 (en) | 2023-10-04 |
Family
ID=63222494
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18762797.1A Active EP3571416B1 (en) | 2017-09-06 | 2018-08-22 | Shrouded centrifugal fan impeller with a periodically and asymmetrically shaped shroud |
Country Status (5)
Country | Link |
---|---|
US (1) | US11143197B2 (en) |
EP (1) | EP3571416B1 (en) |
CN (1) | CN207777266U (en) |
DE (1) | DE102017120537A1 (en) |
WO (1) | WO2019048241A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USD949315S1 (en) * | 2016-06-24 | 2022-04-19 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Vane damper with trailing edge |
DE102020114389A1 (en) * | 2020-05-28 | 2021-12-02 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Fan wheel with seamless connection of the impeller blades to a disc body |
DE102022113706A1 (en) * | 2022-05-31 | 2023-11-30 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Cooling wheel for actively cooling a stator of an electric motor |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008223741A (en) * | 2007-03-16 | 2008-09-25 | Daikin Ind Ltd | Centrifugal blower |
JP5634782B2 (en) * | 2009-08-11 | 2014-12-03 | 山洋電気株式会社 | Centrifugal fan |
JP4902718B2 (en) * | 2009-10-07 | 2012-03-21 | 三菱電機株式会社 | Centrifugal blower and vacuum cleaner |
DE102010009566A1 (en) * | 2010-02-26 | 2011-09-01 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Radial or diagonal fan wheel |
JP5783305B2 (en) | 2013-09-18 | 2015-09-24 | ダイキン工業株式会社 | Gear fluid device |
KR101720491B1 (en) * | 2015-01-22 | 2017-03-28 | 엘지전자 주식회사 | Centrifugal Fan |
KR102257480B1 (en) * | 2015-03-24 | 2021-05-31 | 삼성전자주식회사 | Circular fan |
-
2017
- 2017-09-06 DE DE102017120537.3A patent/DE102017120537A1/en active Pending
-
2018
- 2018-01-05 CN CN201820017251.4U patent/CN207777266U/en active Active
- 2018-08-22 US US16/607,321 patent/US11143197B2/en active Active
- 2018-08-22 WO PCT/EP2018/072693 patent/WO2019048241A1/en unknown
- 2018-08-22 EP EP18762797.1A patent/EP3571416B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2019048241A1 (en) | 2019-03-14 |
EP3571416A1 (en) | 2019-11-27 |
DE102017120537A1 (en) | 2019-03-07 |
US20200080565A1 (en) | 2020-03-12 |
US11143197B2 (en) | 2021-10-12 |
CN207777266U (en) | 2018-08-28 |
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