EP0546361A1 - Axial fan - Google Patents

Axial fan Download PDF

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Publication number
EP0546361A1
EP0546361A1 EP92119783A EP92119783A EP0546361A1 EP 0546361 A1 EP0546361 A1 EP 0546361A1 EP 92119783 A EP92119783 A EP 92119783A EP 92119783 A EP92119783 A EP 92119783A EP 0546361 A1 EP0546361 A1 EP 0546361A1
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EP
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Prior art keywords
blades
blade
axial fan
fan according
hub
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EP92119783A
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German (de)
French (fr)
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EP0546361B1 (en
Inventor
Kurt Dipl.-Ing. Hauser
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans

Definitions

  • the invention relates to an axial fan, in particular for radiators of motor vehicle engines, with an impeller with several asymmetrically arranged fan blades.
  • An impeller for an axial fan is also known (DE 38 32 026 A1), in which one has avoided subjectively disturbing noises by arranging a blade with a shape different from this between two adjacent blades of the same shape.
  • An example provides three blade groups, each with three blades of the same shape, offset at an angle of 120 to one another, the individual blades of which are each arranged in the circumferential direction next to one another in such a way that they are distributed approximately uniformly over the circumference of the hub.
  • the respective blade root has a different length in the circumferential direction. It has been shown that with such an impeller design the frequency of the rotary gear can be reduced, but the rotary sound itself cannot be eliminated.
  • the present invention is therefore based on the object of designing an axial fan of the type mentioned in such a way that the known effect of eliminating the rotary sound can be achieved by asymmetrical division, but without the cooling capacity needing to be reduced.
  • the asymmetrical blade arrangement is only provided in an outer radial area of the blades, while in the inner radial area adjoining the hub, which is particularly advantageous a width of about a third of the radial length the blades can have a radially symmetrical blade arrangement with the same pitch and the same blade design.
  • This design is based on the knowledge that it is sufficient to move the asymmetrical design to the outer area of the drive and to design it according to the criteria known per se, but to leave the design in the inner radial area as in the case of radially symmetrical designs
  • Impellers of conventional design are the case in which all the blades are evenly distributed over the circumference and are of the same design.
  • the number of blades to be used need not be reduced, so that the cooling capacity can remain high.
  • the asymmetrical design is only sufficient in the outer radial area to prevent the unwanted rotary sound.
  • an advantageous further development of the invention results when the angular distance between the center of the outermost blade ends and the center of adjacent blades is different in each case.
  • the division in the outer region changes from blade to blade as a result of this configuration.
  • the blades in the outer region can each be designed differently, so that in this outer radial region the blade shape is also different from blade to blade. It has been shown that the unwanted rotary sound can be eliminated in a particularly advantageous manner by these measures.
  • the invention is illustrated in the drawing using an exemplary embodiment.
  • the only embodiment shows an impeller for an axial fan seen in the flow direction.
  • This impeller (1) consists of a central hub (2) and an outer ring (3) concentrically surrounding this hub, and nine air passages extend between the outer ring (3) and hub (2) shovel (4 to 12). All of these fan blades (4 to 12) have an identically designed blade root (13), each of which extends up to the circular line (14) shown in broken lines.
  • the outer circumference of the hub (2) and this circular line (14) delimit an inner radial region (15) which forms a ring with the width B ; forms.
  • This width B corresponds to about a third of the length I of the blades (4 to 12), this length I being measured radially between the circumference of the hub (2) and the inner circumference (3a) of the outer ring (3).
  • an outer radial area (16) of the impeller (1) is therefore formed, which also forms a ring in plan view, the width B a is.
  • the blades are therefore designed in the same way as in the case of a radially symmetrical fan wheel.
  • both the shape of the individual blades (4 to 12) and their division relative to the outer ring (3) differ.
  • the design has been made so that in the outer radial region (16) an arrangement and design of the blades (4 to 12) is made, which is symmetrical to the plane S, which with the central axis and the central plane through the blade (4) coincides, which runs exclusively radially.
  • the blade (5) adjoining the radially extending blade (4) in the direction of rotation (17) is curved in a crescent shape to the rear against the direction of rotation (17).
  • the blade (12) symmetrical to it is crescent-shaped in the direction of rotation (17) to the front.
  • the blade (6) adjoining the blade (5) in the direction of rotation (17) is also still curved counter to the direction of rotation (17).
  • the curvature is much flatter than that of the blade (5). Accordingly, the curvature of the blade (11), which is symmetrical to the blade (6) and extends in the direction of rotation, is weaker than the curvature of the blade (12).
  • the blade (7) adjoining the blade (6) in the direction of rotation is curved in the shape of a sickle in the direction of rotation, more specifically than the blade (8) adjacent to it in the direction of rotation.
  • the blades (9 and 10) are again symmetrical to the blades (7 and 8) and are therefore crescent-shaped against the direction of rotation, the backward curvature of the blade (9) again being smaller than that of the blade (10).
  • This configuration means that the angular distance between the ends of the blades (4 to 12), measured in the exemplary embodiment on the inner circumference (3a) of the outer ring (3), differs from blade to blade.
  • the angular distance (20) between the center (4a) of the blade (4) and the center (5a) of the adjacent blade (5) in the exemplary embodiment is 32.3 °
  • the distance (21) between the center (5a) is Blade (5) and the center (6a) of the blade (6) adjacent in the direction of rotation is 44.4 ° .
  • the distance (22) between the center (6a) of the blade (6) and the blade (7) adjacent to it in the direction of rotation is 51.1 ° and then follows between the center (7a) of the blade (7) and the center (8a) of the blade (8) an angular distance (23) of 37 °.
  • the centers (8a and 9a) of the blades (8 and 9) are spaced apart by an angular distance (24) of 30.6 ° and then there is again an angular distance (23 ') between the centers of the blades (9 and 10) 37 °.
  • the angular distance (22 ') between the center (10a) of the blade (10) and the center (11a) of the blade (11) adjacent to it in the direction of rotation is not exactly selected according to the distance (22), but only with 50.9 ° and the distance (21 ') is not exactly the same as the distance (21), but is chosen to be somewhat larger at 44.7.
  • the distance (20 ') is also only 32.1 ° in contrast to 32.3 of the distance (20). Nevertheless, the plane S remains essentially the plane of symmetry for the impeller (1), which therefore also has no imbalance and, in addition to a large air output, is also designed in such a way that an annoying rotary sound is avoided.
  • the angular distances (20 to 24, 20 'to 23') can also be varied.
  • the symmetrical structure is also not necessary in every case.
  • the decisive factor is that a completely symmetrical arrangement and design of the blade feet (13) is selected and the asymmetrical arrangement for the purpose of preventing the rotary sound, which is known per se, is only inserted in the outer radial region (16).

Abstract

An impeller is described for the fan of an automobile motor, in which the vanes in the inner radial region (15) adjoining the hub (2) are shaped identically and are distributed uniformly on the hub circumference, while in an outer radial region (16), which starts at a radial distance of approximately one third of the vane length (1) from the hub outwards, they are asymmetric and are disposed so as to be unevenly distributed. This design results in a high capacity, but avoids undesirable rotation-induced sound. <IMAGE>

Description

Die Erfindung betrifft einen Axiallüfter, insbesondere für Kühler von Kraftfahrzeugmotoren, mit einem Laufrad mit mehreren asymmetrisch angeordneten Lüfterschaufeln.The invention relates to an axial fan, in particular for radiators of motor vehicle engines, with an impeller with several asymmetrically arranged fan blades.

Es ist bekannt, daß Axiallüfter der eingangs genannten Art Drehklangspitzen aufweisen, die durch das Zusammenwirken der rotierenden Lüfterschaufeln mit an der Zu- und/oder Abströmseite angeordneten, als Störkörper wirkenden Streben zur Lagerung der Nabe oder Riemenscheiben hervorgerufen werden. Es ist bekannt (R.C. Mellin und G. Sovran, Journal of Basic Engineering, März 1970, S. 143 bis 154), daß man diesen Drehklang durch eine asymmetrische Anordnung, d.h. durch eine ungleiche Verteilung der Schaufelblätter über den Umfang vermeiden kann. Ein Nachteil einer solchen unsymmetrichen Schaufelteilung ist es, daß die Anzahl der Schaufeln verringert werden muß (z.B. auf sieben anstelle von neun Schaufeln), wenn eine Schaufelüberdeckung vermieden werden soll. Die Luft- bzw. Kühlleistung wird dadurch deutlich verschlechtert.It is known that axial fans of the type mentioned at the outset have rotary sound peaks which are caused by the interaction of the rotating fan blades with struts for supporting the hub or pulleys which are arranged on the inflow and / or outflow side and act as disruptive bodies. It is known (R.C. Mellin and G. Sovran, Journal of Basic Engineering, March 1970, pp. 143-154) that this rotary sound can be obtained by an asymmetrical arrangement, i.e. can avoid by uneven distribution of the blades over the circumference. A disadvantage of such unbalanced blade division is that the number of blades must be reduced (e.g. to seven instead of nine blades) if blade overlap is to be avoided. This significantly worsens the air or cooling performance.

Es ist zwar auch ein Laufrad für einen Axiallüfter bekannt (DE 38 32 026 A1), bei dem man subjektiv störende Geräusche dadurch vermieden hat, daß zwischen zwei einander benachbarten Flügeln gleicher Gestalt ein Flügel mit einer von dieser abweichenden Gestalt angeordnet wird. Ein Beispiel sieht dabei drei Schaufelgruppen mit jeweils drei unter einem Winkel von 120 zueinander versetzten Schaufeln gleicher Gestalt vor, deren einzelne Schaufeln jeweils in Umfangsrichtung nebeneinander so angeordnet sind, daß sie auf dem Umfang der Nabe in etwa gleichmäßig verteilt sind. Der jeweilige Schaufelfuß allerdings besitzt jeweils eine unterschiedliche Länge in Umfangsrichtung. Es hat sich gezeigt, daß man mit einer solchen Laufradausbildung die Frequenz des Drehganges zwar erniedrigen, den Drehklang selbst aber nicht beseitigen kann.An impeller for an axial fan is also known (DE 38 32 026 A1), in which one has avoided subjectively disturbing noises by arranging a blade with a shape different from this between two adjacent blades of the same shape. An example provides three blade groups, each with three blades of the same shape, offset at an angle of 120 to one another, the individual blades of which are each arranged in the circumferential direction next to one another in such a way that they are distributed approximately uniformly over the circumference of the hub. However, the respective blade root has a different length in the circumferential direction. It has been shown that with such an impeller design the frequency of the rotary gear can be reduced, but the rotary sound itself cannot be eliminated.

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, einen Axiallüfter der eingangs genannten Art so auszubilden, daß durch asymmetrische Teilung der bekannte Effekt der Beseitigung des Drehklanges erreichbar ist, ohne daß jedoch die Kühlleistung verringert zu werden braucht.The present invention is therefore based on the object of designing an axial fan of the type mentioned in such a way that the known effect of eliminating the rotary sound can be achieved by asymmetrical division, but without the cooling capacity needing to be reduced.

Zur Lösung dieser Aufgabe wird bei einem Axiallüfter der eingangs genannten Art vorgesehen, daß die asymmetrische Schaufelanordnung erst in einem äußeren Radialbereich der Schaufeln vorgesehen ist, während in dem an die Nabe anschließenden inneren Radialbereich, der besonders vorteilhaft eine Breite von etwa einem Drittel der radialen Länge der Schaufeln besitzen kann, eine radialsymmetrische Schaufelanordnung mit gleicher Teilung und gleicher Schaufelausbildung vorliegt. Diese Ausgestaltung geht dabei von der Erkenntnis aus, daß es ausreichend ist, die asymmetrische Ausgestaltung auf den äußeren Bereich des Laufwerkes zu verlegen und sie nach den an sich bekannten Kriterien zu gestalten, im inneren Radialbereich aber die Ausgestaltung so zu belassen, wie bei radialsymmetrisch aufgebauten Laufrädern üblicher Bauart der Fall ist, bei der alle Schaufeln gleichmäßig auf dem Umfang verteilt und auch gleich ausgebildet sind.To solve this problem it is provided in an axial fan of the type mentioned that the asymmetrical blade arrangement is only provided in an outer radial area of the blades, while in the inner radial area adjoining the hub, which is particularly advantageous a width of about a third of the radial length the blades can have a radially symmetrical blade arrangement with the same pitch and the same blade design. This design is based on the knowledge that it is sufficient to move the asymmetrical design to the outer area of the drive and to design it according to the criteria known per se, but to leave the design in the inner radial area as in the case of radially symmetrical designs Impellers of conventional design are the case in which all the blades are evenly distributed over the circumference and are of the same design.

Durch diese Maßnahme braucht die Anzahl der einzusetzenden Schaufeln nicht verringert zu werden, so daß die Kühlleistung hoch bleiben kann. Dennoch reicht überraschenderweise die asymmetrische Ausgestaltung nur im äußeren Radialbereich aus, um den unerwünschten Drehklang zu unterbinden.With this measure, the number of blades to be used need not be reduced, so that the cooling capacity can remain high. Surprisingly, however, the asymmetrical design is only sufficient in the outer radial area to prevent the unwanted rotary sound.

Nach den Merkmalen des Anspruches 3 ergibt sich eine vorteilhalfte Weiterbildung der Erfindung dann, wenn der Winkelabstand der Mitte der äußersten Schaufelenden zu der Mitte von benachbarten Schaufeln jeweils unterschiedlich ist. Die Teilung im äußeren Bereich ändert sich durch diese Ausgestaltung von Schaufel zu Schaufel. Nach den Merkmalen des Anspruches 4 können die Schaufeln im äußeren Bereich jeweils unterschiedlich ausgebildet sein, so daß in diesem äußeren Radialbereich auch die Schaufelform von Schaufel zu Schaufel unterschiedlich ist. Es hat sich gezeigt, daß durch diese Maßnahmen in besonders vorteilhafter Weise der unerwünschte Drehklang beseitigt werden kann.According to the features of claim 3, an advantageous further development of the invention results when the angular distance between the center of the outermost blade ends and the center of adjacent blades is different in each case. The division in the outer region changes from blade to blade as a result of this configuration. According to the features of claim 4, the blades in the outer region can each be designed differently, so that in this outer radial region the blade shape is also different from blade to blade. It has been shown that the unwanted rotary sound can be eliminated in a particularly advantageous manner by these measures.

In Weiterbildung der Erfindung wird bei einem Axiallüfter mit unterschiedlich gekrümmten Schaufeln jeweils ein Paar von entgegen der Laufrichtung gekrümmten Schaufeln mit einem Paar abwechselnd angeordnet, das in der Laufrichtung gekrümmte Schaufeln aufweist. Nach Anspruch 6 kann in Weiterbildung zwischen zwei entgegengesetzt zueinander gekrümmten Schaufelpaaren eine ausschließlich radial verlaufende Schaufel angeordnet sein, wie dies im Anspruch 6 zum Ausdruck kommt und schließlich ist es nach den Merkmalen des Anspruches 7, z.B. bei einem Laufrad mit vier gekrümmten Schaufelpaaren und mit einer radial verlaufenden Schaufel, vorteilhaft, die Mittelebene der radial verlaufenden Schaufel im wesentlichen als eine Symmetrieebene für die gesamte Schaufelanordnung und -ausbildung im äußeren Radialbereich auszubilden. Diese im Anspruch 7 umrissenen Merkmale bringen den Vorteil mit sich, daß das Laufrad keine Unwuchten aufweist.In a further development of the invention, in the case of an axial fan with differently curved blades, a pair of blades curved counter to the direction of rotation is alternately arranged with a pair which has blades curved in the direction of rotation. According to claim 6, in a further development, an exclusively radially extending blade can be arranged between two oppositely curved pairs of blades, as is expressed in claim 6, and finally, according to the features of claim 7, e.g. in the case of an impeller with four curved pairs of blades and with a radial blade, it is advantageous to design the central plane of the radial blade essentially as a plane of symmetry for the entire blade arrangement and design in the outer radial region. These features outlined in claim 7 have the advantage that the impeller has no imbalances.

Die Erfindung ist in der Zeichnung anhand eines Ausführungsbeispieles dargestellt. Das einzige Ausführungsbeispiel zeigt dabei ein Laufrad für einen Axiallüfter in der Durchströmrichtung gesehen.The invention is illustrated in the drawing using an exemplary embodiment. The only embodiment shows an impeller for an axial fan seen in the flow direction.

Dieses Laufrad (1) besteht aus einer zentralen Nabe (2) und einem diese Nabe konzentrisch umgebenden Außenring (3), und es erstrecken sich zwischen Außenring (3) und Nabe (2) neun Lüfterschaufeln (4 bis 12). Alle diese Lüfterschaufeln (4 bis 12) besitzen einen identisch ausgebildeten Schaufelfuß (13), der jeweils bis zu der strichpunktiert gezeigten Kreislinie (14) verläuft. Der äußere Umfang der Nabe (2) und diese Kreislinie (14) grenzen dabei einen inneren Radialbereich (15) ab, der einen Ring mit der Breite B; bildet. Diese Breite B; entspricht etwa einem Drittel der Länge I der Schaufeln (4 bis 12), wobei diese Länge I radial zwischen dem Umfang der Nabe (2) und dem inneren Umfang (3a) des Außenringes (3) gemessen ist. In dem Bereich zwischen dem inneren Umfang (3a) des Außenringes (3) und der strichpunktierten Kreislinie (14) wird daher ein äußerer Radialbereich (16) des Laufrades (1) gebildet, der ebenfalls in der Draufsicht einen Ring bildet, dessen Breite Ba beträgt.This impeller (1) consists of a central hub (2) and an outer ring (3) concentrically surrounding this hub, and nine air passages extend between the outer ring (3) and hub (2) shovel (4 to 12). All of these fan blades (4 to 12) have an identically designed blade root (13), each of which extends up to the circular line (14) shown in broken lines. The outer circumference of the hub (2) and this circular line (14) delimit an inner radial region (15) which forms a ring with the width B ; forms. This width B ; corresponds to about a third of the length I of the blades (4 to 12), this length I being measured radially between the circumference of the hub (2) and the inner circumference (3a) of the outer ring (3). In the area between the inner circumference (3a) of the outer ring (3) and the dash-dotted circular line (14), an outer radial area (16) of the impeller (1) is therefore formed, which also forms a ring in plan view, the width B a is.

Alle Schaufelfüße (13) der Schaufeln (4 bis 12), die wie bereits erwähnt untereinander identisch sind, sind gleichmäßig auf dem Umfang der Nabe (2) verteilt angeordnet, so daß bei dem gezeigten Ausführungsbeispiel mit neun Schaufeln (4 bis 12) jeder gleiche Punkt des Schaufelfußes an der Nabenoberfläche, z.B. also auch die jeweils angedeutete Mitte der Schaufeln (4 bis 12) von dem zugeordneten benachbarten Punkt bzw. von der benachbarten Mitte der angrenzenden Schaufel um einen Winkelabstand zueinander versetzt sind, der sich aus jeweils dem gleichen Winkel a von 40* ergibt. In dem radial inneren Bereich (15), der an die Nabe (2) angrenzt, ist daher die Ausgestaltung der Schaufeln ausgelegt wie bei einem radialsymmetrisch aufgebauten Lüfterrad.All blade feet (13) of the blades (4 to 12), which, as already mentioned, are identical to one another, are arranged evenly distributed over the circumference of the hub (2), so that in the embodiment shown with nine blades (4 to 12), each is the same Point of the blade root on the hub surface, e.g. So the indicated center of the blades (4 to 12) are offset from the associated adjacent point or from the adjacent center of the adjacent blade by an angular distance from each other, which results from the same angle a of 40 *. In the radially inner region (15), which adjoins the hub (2), the blades are therefore designed in the same way as in the case of a radially symmetrical fan wheel.

Im äußeren Radialbereich (16) dagegen weicht sowohl die Form der einzelnen Schaufeln (4 bis 12) als auch deren Teilung gegenüber dem Außenring (3) voneinander ab. Beim Ausführungsbeispiel ist allerdings die Ausgestaltung so vorgenommen worden, daß in dem äußeren Radialbereich (16) eine Anordnung und Ausbildung der Schaufeln (4 bis 12) vorgenommen ist, die symmetrisch zu der Ebene S ist, welche mit der Mittelachse und der Mittelebene durch die Schaufel (4) zusammenfällt, die ausschließlich radial verläuft. Die in der Drehrichtung (17) an die radial verlaufende Schaufel (4) angrenzende Schaufel (5) ist entgegen der Drehrichtung (17) sichelförmig nach hinten gekrümmt. Entsprechend ist die zu ihr symmetrische Schaufel (12) sichelförmig in der Drehrichtung (17) nach vorne gekrümmt. Der die Schaufel (5) in der Drehrichtung (17) angrenzende Schaufel (6) ist ebenfalls noch entgegen der Drehrichtung (17) gekrümmt. Die Krümmung ist allerdings wesentlich flacher als jene der Schaufel (5). Entsprechend ist auch die Krümmung der Schaufel (11), die symmetrisch zu der Schaufel (6) ist, und in der Drehrichtung verläuft, schwächer als die Krümmung der Schaufel (12).In the outer radial region (16), on the other hand, both the shape of the individual blades (4 to 12) and their division relative to the outer ring (3) differ. In the embodiment, however, the design has been made so that in the outer radial region (16) an arrangement and design of the blades (4 to 12) is made, which is symmetrical to the plane S, which with the central axis and the central plane through the blade (4) coincides, which runs exclusively radially. The blade (5) adjoining the radially extending blade (4) in the direction of rotation (17) is curved in a crescent shape to the rear against the direction of rotation (17). Correspondingly, the blade (12) symmetrical to it is crescent-shaped in the direction of rotation (17) to the front. The blade (6) adjoining the blade (5) in the direction of rotation (17) is also still curved counter to the direction of rotation (17). However, the curvature is much flatter than that of the blade (5). Accordingly, the curvature of the blade (11), which is symmetrical to the blade (6) and extends in the direction of rotation, is weaker than the curvature of the blade (12).

Die an die Schaufel (6) in der Drehrichtung angrenzende Schaufel (7) ist in der Drehrichtung sichelförmig gekrümmt, und zwar mehr als die ihr in der Drehrichtung benachbarte Schaufel (8). Symmetrisch zu den Schaufeln (7 und 8) sind wieder die Schaufeln (9 und 10) ausgebildet, die daher entgegen der Drehrichtung sichelförmig gekrümmt sind, wobei die Rückwärtskrümmung der Schaufel (9) wieder kleiner ist als jene der Schaufel (10).The blade (7) adjoining the blade (6) in the direction of rotation is curved in the shape of a sickle in the direction of rotation, more specifically than the blade (8) adjacent to it in the direction of rotation. The blades (9 and 10) are again symmetrical to the blades (7 and 8) and are therefore crescent-shaped against the direction of rotation, the backward curvature of the blade (9) again being smaller than that of the blade (10).

Diese Ausgestaltung führt dazu, daß der Winkelabstand zwischen den Enden der Schaufeln (4 bis 12), beim Ausführungsbeispiel gemessen am inneren Umfang (3a) des Außenringes (3) unterschiedlich ist, und zwar von Schaufel zu Schaufel. So beträgt der Winkelabstand (20) zwischen der Mitte (4a) der Schaufel (4) und der Mitte (5a) der benachbarten Schaufel (5) beim Ausführungsbeispiel 32,3°, während der Abstand (21) zwischen der Mitte (5a) der Schaufel (5) und der Mitte (6a) der in Drehrichtung benachbarten Schaufel (6) 44,4 ° beträgt. Der Abstand (22) zwischen der Mitte (6a) der Schaufel (6) und der ihr in der Drehrichtung benachbarten Schaufel (7) beträgt 51,1 ° und es folgt dann zwischen der Mitte (7a) der Schaufel (7) und er Mitte (8a) der Schaufel (8) ein Winkelabstand (23) von 37 °. Die Mitten (8a bzw. 9a) der Schaufeln (8 und 9) liegen um einen Winkelabstand (24) von 30,6° auseinander und es folgt dann zwischen den Mitten der Schaufeln (9 und 10) wieder ein Winkelabstand (23') von 37°. Der Winkelabstand (22') zwischen der Mitte (10a) der Schaufel (10) und der Mitte (11 a) der ihr in der Drehrichtung benachbarten Schaufel (11) ist nun allerdings nicht exakt dem Abstand (22) entsprechend gewählt, sondern nur mit 50,9° und der Abstand (21') beträgt auch nicht exakt das gleiche wie der Abstand (21), sondern ist etwas größer mit 44,7 gewählt. Auch der Abstand (20') beträgt nur 32,1 ° im Gegensatz zu 32,3 des Abstandes (20). Trotzdem bleibt die Ebene S im wesentlichen die Symmetrieebene für das Laufrad (1), das dadurch auch keine Unwuchten aufweist und neben einer grossen Luftleistung auch so ausgelegt ist, daß ein störender Drehklang vermieden wird.This configuration means that the angular distance between the ends of the blades (4 to 12), measured in the exemplary embodiment on the inner circumference (3a) of the outer ring (3), differs from blade to blade. The angular distance (20) between the center (4a) of the blade (4) and the center (5a) of the adjacent blade (5) in the exemplary embodiment is 32.3 ° , while the distance (21) between the center (5a) is Blade (5) and the center (6a) of the blade (6) adjacent in the direction of rotation is 44.4 ° . The distance (22) between the center (6a) of the blade (6) and the blade (7) adjacent to it in the direction of rotation is 51.1 ° and then follows between the center (7a) of the blade (7) and the center (8a) of the blade (8) an angular distance (23) of 37 °. The centers (8a and 9a) of the blades (8 and 9) are spaced apart by an angular distance (24) of 30.6 ° and then there is again an angular distance (23 ') between the centers of the blades (9 and 10) 37 °. The angular distance (22 ') between the center (10a) of the blade (10) and the center (11a) of the blade (11) adjacent to it in the direction of rotation is not exactly selected according to the distance (22), but only with 50.9 ° and the distance (21 ') is not exactly the same as the distance (21), but is chosen to be somewhat larger at 44.7. The distance (20 ') is also only 32.1 ° in contrast to 32.3 of the distance (20). Nevertheless, the plane S remains essentially the plane of symmetry for the impeller (1), which therefore also has no imbalance and, in addition to a large air output, is also designed in such a way that an annoying rotary sound is avoided.

Selbstverständlich können die Winkelabstände (20 bis 24, 20' bis 23') auch variiert werden. Der symmetrische Aufbau ist auch nicht in jedem Fall notwendig. Maßgebend ist, daß eine vollkommen symmetrische Anordnung und Ausbildung der Schaufelfüße (13) gewählt wird und die asymmetrische Anordnung zum Zweck der Unterbindung des Drehklanges, die an sich bekannt ist, nur in dem äußeren Radialbereich (16) hereingelegt wird.Of course, the angular distances (20 to 24, 20 'to 23') can also be varied. The symmetrical structure is also not necessary in every case. The decisive factor is that a completely symmetrical arrangement and design of the blade feet (13) is selected and the asymmetrical arrangement for the purpose of preventing the rotary sound, which is known per se, is only inserted in the outer radial region (16).

Claims (8)

1. Axiallüfter, insbesondere für Kühler von Kraftfahrzeugmotoren, mit einem Laufrad (1) mit einer Nabe (2) und mit mehreren asymmetrisch angeordneten Lüfterschaufeln (4 bis 12), dadurch gekennzeichnet, daß die asymmetrische Schaufelanordnung mit ungleicher Teilung nur in einem äußeren Radialbereich (16) der Schauteln (4 bis 12) vorgesehen ist, während in dem an die Nabe (2) anschließenden inneren Radialbereich (15) eine radialsymmetrische Schaufelanordnung mit gleicher Teilung und gleicher Schaufelausbildung vorliegt.1. Axial fan, especially for radiators of motor vehicle engines, with an impeller (1) a hub (2) and with several asymmetrically arranged fan blades (4 to 12), characterized in that the asymmetrical blade arrangement with an uneven pitch is only provided in an outer radial region (16) of the blades (4 to 12), while in the Hub (2) adjoining the inner radial region (15) there is a radially symmetrical blade arrangement with the same pitch and the same blade design. 2. Axiallüfter nach Anspruch 1, dadurch gekennzeichnet, daß der innere Radialbereich (15) eine Breite B; von etwa einem Drittel der radialen Länge I der Schaufeln (4 bis 12) aufweist.2. Axial fan according to claim 1, characterized in that the inner radial region (15) has a width B ; of about a third of the radial length I of the blades (4 to 12). 3. Axiallüfter nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß der Winkelabstand (20 bis 24) der Mitten (4a bis 12a) der äußersten Schaufelenden zu der Mitte von benachbarten Schaufeln jeweils unterschiedlich ist.3. Axial fan according to claims 1 and 2, characterized in that the angular distance (20 to 24) of the centers (4a to 12a) of the outermost blade ends is different from the center of adjacent blades. 4. Axiallüfter nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Schaufeln im äußeren Radialbereich (16) jeweils unterschiedlich ausgebildet sind.4. Axial fan according to one of claims 1 to 3, characterized in that the blades in the outer radial region (16) are each designed differently. 5. Axiallüfter nach Anspruch 4, dadurch gekennzeichnet, daß jeweils ein Paar von entgegen der Laufrichtung (17) gekrümmten Schaufeln (5, 6) mit einem Paar in der Laufrichtung (17) gekrümmter Schaufeln (7, 8) abwechseln.5. Axial fan according to claim 4, characterized in that in each case a pair of blades (5, 6) curved against the direction of rotation (17) alternate with a pair of blades (7, 8) curved in the direction of rotation (17). 6. Axiallüfter nach Anspruch 5, dadurch gekennzeichnet, daß zwischen zwei entgegengesetzt zueinander gekrümmten Schaufelpaaren (5, 6, bzw. 11, 12) eine ausschließlich radial verlaufende Schaufel (4) angeordnet ist.6. Axial fan according to claim 5, characterized in that an exclusively radially extending blade (4) is arranged between two oppositely curved pairs of blades (5, 6 or 11, 12). 7. Axiallüfter nach Anspruch 6, dadurch gekennzeichnet, daß die Mittelebene S der radial verlaufenden Schaufel (4) im wesentlichen eine Symmetrieebene für die Schaufelanordnung und -ausbildung im äußeren Radialbereich (16) bildet.7. Axial fan according to claim 6, characterized in that the center plane S of the radially extending blade (4) essentially forms a plane of symmetry for the blade arrangement and formation in the outer radial region (16). 8. Axiallüfter nach Anspruch 1 oder einem der übrigen Ansprüche, dadurch gekennzeichnet, daß die äußeren Enden der Lüfterschaufeln (4 bis 12) an einem mitumlaufenden Außenring (3) befestigt sind.8. Axial fan according to claim 1 or one of the other claims, characterized in that the outer ends of the fan blades (4 to 12) are attached to a rotating outer ring (3).
EP92119783A 1991-12-12 1992-11-20 Axial fan Expired - Lifetime EP0546361B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4140987A DE4140987A1 (en) 1991-12-12 1991-12-12 AXIAL FAN
DE4140987 1991-12-12

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EP0546361B1 EP0546361B1 (en) 1995-09-06

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GB2302141A (en) * 1995-06-13 1997-01-08 Lg Electronics Inc Axial flow fan for microwave oven
WO2011032867A1 (en) * 2009-09-17 2011-03-24 Behr Gmbh & Co. Kg Fan for an internal combustion engine
US20160090899A1 (en) * 2014-09-29 2016-03-31 Ford Global Technologies, Llc Enhanced charge air cooler
CN107218249A (en) * 2017-08-01 2017-09-29 曹建礼 Fan wheel Reinforced Hoop

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DE102004017727A1 (en) 2003-04-19 2004-11-04 Ebm-Papst St. Georgen Gmbh & Co. Kg Fan for equipment comprises an air-conveying channel containing a fan wheel rotating about a central axis and having a central hub with an outer periphery on which fan blades are fixed
CN105066124A (en) * 2015-08-14 2015-11-18 吉首大学 Tail heat utilization type dust retention preventing oil burning boiler
CN105066085A (en) * 2015-08-14 2015-11-18 吉首大学 Tail heat utilizing type oil burning boiler capable of preventing dust deposition
DE102020004255A1 (en) 2020-07-15 2022-01-20 Daimler Ag Turbine wheel for a turbine of an exhaust gas turbocharger

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JPH0261399A (en) * 1988-08-26 1990-03-01 Calsonic Corp Axial flow fan
DE3832026A1 (en) * 1988-09-21 1990-03-22 Bosch Gmbh Robert FAN WHEEL
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2302141A (en) * 1995-06-13 1997-01-08 Lg Electronics Inc Axial flow fan for microwave oven
GB2302141B (en) * 1995-06-13 1997-10-22 Lg Electronics Inc Axial flow fan for microwave oven
WO2011032867A1 (en) * 2009-09-17 2011-03-24 Behr Gmbh & Co. Kg Fan for an internal combustion engine
US20160090899A1 (en) * 2014-09-29 2016-03-31 Ford Global Technologies, Llc Enhanced charge air cooler
US9739195B2 (en) * 2014-09-29 2017-08-22 Ford Global Technologies, Llc Enhanced charge air cooler
CN107218249A (en) * 2017-08-01 2017-09-29 曹建礼 Fan wheel Reinforced Hoop

Also Published As

Publication number Publication date
ES2076655T3 (en) 1995-11-01
DE4140987A1 (en) 1993-06-17
DE59203578D1 (en) 1995-10-12
EP0546361B1 (en) 1995-09-06

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