EP0261490A1 - Radial fan - Google Patents

Radial fan Download PDF

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Publication number
EP0261490A1
EP0261490A1 EP87113062A EP87113062A EP0261490A1 EP 0261490 A1 EP0261490 A1 EP 0261490A1 EP 87113062 A EP87113062 A EP 87113062A EP 87113062 A EP87113062 A EP 87113062A EP 0261490 A1 EP0261490 A1 EP 0261490A1
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EP
European Patent Office
Prior art keywords
fan
spokes
shaft
fan wheel
wheel
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Granted
Application number
EP87113062A
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German (de)
French (fr)
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EP0261490B1 (en
Inventor
Heinrich Dipl.-Ing. Kirchner
Udo Dr. Winter
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Siemens AG
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Siemens AG
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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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans

Definitions

  • the invention relates to a radial fan according to the preamble of claim 1; such a radial fan is known from US-PS 22 75 564.
  • a radial blower in particular for use in heating and air conditioning systems of motor vehicles, is also known, in which a fan wheel is fastened on one motor shaft end, in which the intermediate piece between the hub fastened with the fan shaft on the one hand and the Fan blade ring, on the other hand, is provided with openings which leave spokes between them, which are intended to form a bundle of springs connected in parallel.
  • a radial fan is to be created with two fan wheels arranged axially one behind the other or directly on a shaft, each with a fan blade ring held at a radial distance from a fan wheel hub fastened to the fan shaft, which allows a significant reduction in operating noise despite the high power yield.
  • the radial fan according to the invention allows, on the one hand, through its perforated spoke plane of the fan wheels, an air distribution distribution of the air flow sucked in at both end faces of each fan wheel over the entire axial outlet width of each fan blade ring and, on the other hand, a low fan operating noise, since the operating noise, which also determines the operating noise, is a result of the interaction forces resulting from both fan wheels can mutually compensate for one another due to the mutual phase shift and therefore cannot have an effect.
  • the fan wheel shape may differ slightly from the ideal circular shape and the spokes as the outer contour may result in a polygon corresponding to the number of spokes, due to the vibrating forces per se on the fan shaft would act;
  • the offset of the two fan wheels according to the invention advantageously ensures that the overall vibrating forces acting on the fan shaft largely compensate for one another.
  • FIG. 1 shows the axial top view of the fan wheel drive arrangement of a radial fan provided for heating or air conditioning systems of motor vehicles.
  • a first fan wheel 2 is fixedly mounted on the right motor shaft end of a commutator motor 1 and a second fan wheel 3 is fixedly mounted on the left motor shaft end of the commutator motor 1.
  • the motor shaft thus simultaneously serves as a fan shaft 4.
  • Both fan wheels 2 and 3 are surrounded by a spiral housing as an air duct housing in a manner which is not shown here but is generally known.
  • the armature winding of the permanent magnet-excited commutator motor 1 is fed by an electrical supply line 13 via brush holders 11, 12.
  • FIGS. 2 and 3 each show a top view of the respective axially outer end face of the fan wheels 2 and 3, which are injection-molded in one piece from plastic as identical unit components.
  • Each Fan wheel 2, 3 has a hub 26 or 36 for fastening the fan wheel on the fan shaft 4, a fan blade ring 21 or 31 and for connection between the hub 4 and the fan blade ring 21 or 31, which are held at a radial distance, four each in a spoke plane S1 or S2 lying spokes 22-25 or 32-35, of which only the spokes 22, 23 of the right fan wheel 2 are visible in FIG. 2 and only the spokes 32-34 of the left fan wheel 3 are visible in FIG.
  • the spoke planes S1 and S2 of each fan wheel 2 and 3 are located axially centrally between the end faces of their fan wheels in terms of construction and mass balance. Openings are provided in the spoke planes S1 and S2 between the spokes 22-25 and 32-35, respectively, so that an axial air flow compensation of the air flows entering on both end faces of each fan wheel in the sense of a uniform full loading of the outlet side of the fan wheel despite the possibly by the central drive motor impeded air entry can take place on the inner end faces of the drive motor 1 facing each fan wheel 2 or 3.
  • the two identical fan wheels 2 and 3 designed as a unit component, are fastened on the common fan shaft 4 in such a way that, viewed in the axial direction, they are offset from one another by a gap by the circumferential angle of rotation.
  • the circumferential angle of rotation 45 °.

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

Abstract

Bei einem Radialventilator mit zwei axial hintereinander auf je einem Wellenende des zwischenliegenden Antriebsmotors (1) befestigten Lüfterrädern (2 bzw.3) mit je einem in radialem Abstand zur lüfterwellenseitigen Nabe (26 bzw.36) gehaltenem Lüfterschaufelkranz (21 bzw.31) soll mit einfachen Mitteln trotz hoher Leistungsausbeute das Betriebsgeräusch gesenkt werden; dazu wird vorgeschlagen, den Lüfterschaufelkranz (21 bzw.31) jedes Lüfterrades (2 bzw.3) über Speichen (22-25 bzw.32-35) unter Freilassung von tangentialen Zwischenräumen mit der Nabe (26 bzw.36) zu verbinden und in Achsrichtung (Lüfterwelle 4) gesehen die Speichen (22-25) des einen Lüfterrades (2) relativ zu den Speichen (32-35) des anderen Lüfterrades (3) auf Lücke (Verdrehungs-Umfangswinkel ) in Umfangsrichtung gegeneinander versetzt anzuordnen.In the case of a radial fan with two fan wheels (2 or 3) fastened axially one behind the other on one shaft end of the intermediate drive motor (1), each with a fan blade ring (21 or 31) held at a radial distance from the fan shaft-side hub (26 or 36) simple means the operating noise can be reduced despite high power yield; for this purpose, it is proposed to connect the fan blade ring (21 or 31) of each fan wheel (2 or 3) via spokes (22-25 or 32-35) to the hub (26 or 36) while leaving tangential gaps and in Axial direction (fan shaft 4) seen the spokes (22-25) of one fan wheel (2) relative to the spokes (32-35) of the other fan wheel (3) on a gap (circumferential angle of rotation) staggered in the circumferential direction.

Description

Die Erfindung bezieht sich auf einen Radialventilator gemäß Oberbegriff des Anspruchs 1; ein derartiger Radialventilator ist durch die US-PS 22 75 564 bekannt.The invention relates to a radial fan according to the preamble of claim 1; such a radial fan is known from US-PS 22 75 564.

Durch die DE-PS 29 39 385 ist weiterhin ein Radialgebläse, insbesondere zum Einsatz für Heiz- und Klimaanlagen von Kraftfahrzeugen bekannt, bei dem auf dem einen Motorwellenende ein Lüfterrad befestigt ist, bei dem das Zwischenstück zwischen der mit der Lüfterwelle befestigten Nabe einerseits und dem Lüfterschaufelkranz andererseits mit Durchbrechungen versehen ist, die zwischen sich Speichen belassen, die ein Bündel von parallel geschalteten Federn bilden sollen.From DE-PS 29 39 385 a radial blower, in particular for use in heating and air conditioning systems of motor vehicles, is also known, in which a fan wheel is fastened on one motor shaft end, in which the intermediate piece between the hub fastened with the fan shaft on the one hand and the Fan blade ring, on the other hand, is provided with openings which leave spokes between them, which are intended to form a bundle of springs connected in parallel.

Durch die DE-OS 20 43 175 ist ein geräuschgedämpftes Radialgebläse bekannt, dessen geschlossene mittige Nabenscheibe beidseitig mit zusätzlichen Radialflügeln besetzt ist, die auf der einen Nabenscheibenseite gegenüber denen auf der anderen Nabenscheibenseite, vorzugsweise um eine halbe Flügelteilung, versetzt angeordnet sind.From DE-OS 20 43 175 a noise-dampened radial fan is known, the closed central hub disc is occupied on both sides with additional radial vanes, which are offset on one side of the hub disc compared to those on the other side of the hub disc, preferably by half a blade pitch.

Gemäß Aufgabe vorliegender Erfindung soll ein Radialventilator mit zwei axial hintereinander mittelbar bzw. unmittelbar auf einer Welle angeordneten Lüfterrädern mit jeweils in radialem Abstand zu einer auf der Lüfterwelle befestigten Lüfterradnabe gehaltenen Lüfterschaufelkranz geschaffen werden, der trotz hoher Leistungsausbeute eine wesentliche Verminderung des Betriebsgeräusches erlaubt.According to the object of the present invention, a radial fan is to be created with two fan wheels arranged axially one behind the other or directly on a shaft, each with a fan blade ring held at a radial distance from a fan wheel hub fastened to the fan shaft, which allows a significant reduction in operating noise despite the high power yield.

Die Lösung dieser Aufgabe gelingt bei einem Radialventilator der eingangs genannten Art erfindungsgemäß durch die Lehre des Anspruchs 1; vorteilhafte Ausgestaltung der Erfindung sind jeweils Gegenstand der Unteransprüche.This object is achieved in a radial fan of the type mentioned in the invention by the teaching of claim 1; advantageous embodiments of the invention are the subject of the dependent claims.

Der erfindungsgemäße Radialventilator erlaubt einerseits durch seine mit Durchbrechungen versehenen Speichenebene der Lüfterräder eine Luftführungsverteilung der an beiden Stirnseiten jedes Lüfterrades angesaugten Luftströmung über die gesamte axiale Austrittsbreite jedes Lüfterschaufelkranzes und andererseits ein trotzdem niedriges Lüfter-Betriebsgeräusch, da sich die das Betriebsgeräusch mitbestimmenden, aus dem Zusamemnwirken der beiden Lüfterräder ergebenden Kräfte durch die gegenseitige Phasenverschiebung gegenseitig kompen- und somit nicht auswirken können.The radial fan according to the invention allows, on the one hand, through its perforated spoke plane of the fan wheels, an air distribution distribution of the air flow sucked in at both end faces of each fan wheel over the entire axial outlet width of each fan blade ring and, on the other hand, a low fan operating noise, since the operating noise, which also determines the operating noise, is a result of the interaction forces resulting from both fan wheels can mutually compensate for one another due to the mutual phase shift and therefore cannot have an effect.

Dieser Lösung liegt die Erkenntnis zugrunde, daß bedingt durch den Fertigungsprozeß der zweckmäßigerweise einstückig aus Kunststoff gespritzten Lüfterräder die Lüfterradform geringfügig von der idealen Kreisform abweichen und sich durch die Speichen als Außenkontur ein Vieleck entsprechend der Speichenzahl ergeben kann, aufgrund der an sich Rüttelkräfte auf die Lüfterwelle einwirken würden; jedoch durch den erfindungsgemäßen Versatz der beiden Lüfterräder in vorteilhafter Weise erreicht wird, daß sich die insgesamt auf die Lüfterwelle einwirkenden Rüttelkräfte weitgehend gegenseitig kompensieren. Darüber hinaus wird auch eine wesentliche Minderung der Luftströmungsgeräusche dadurch erreicht, daß die aufgrund der Durchbrechungen in den Speichenebenen an sich zu befürchtenden axialen Luftströmungen zwischen den beiden Lüfterrädern weitgehend vermieden werden, da einerseits zwar ein axialer Verteilungsstrom der angesaugten Luft zu der Luftaustrittsseite innerhalb eines einzelnen Lüfterrades aufgrund der Durchbrechungen in der Speichenebene in vorteilhafter Weise möglich ist, jedoch ein an sich unerwünschter axialer Luftstrom zwischen den beiden Lüfterrädern aufgrund des gegenseitigen Versatzes der Lüfterräder auf Lücke und des dadurch verminderten axialen Strömungsquerschnittes zwischen den inneren Stirnseiten der beiden axial hintereinander angeordneten Lüfterrädern verhindert wird.This solution is based on the knowledge that, due to the manufacturing process of the fan wheels, which are expediently injection-molded in one piece from plastic, the fan wheel shape may differ slightly from the ideal circular shape and the spokes as the outer contour may result in a polygon corresponding to the number of spokes, due to the vibrating forces per se on the fan shaft would act; However, the offset of the two fan wheels according to the invention advantageously ensures that the overall vibrating forces acting on the fan shaft largely compensate for one another. In addition, a substantial reduction in the air flow noise is achieved in that the axial air flows between the two fan wheels, which are to be feared as a result of the openings in the spoke planes, are largely avoided, since on the one hand an axial distribution flow of the sucked-in air to the air outlet side within a single fan wheel due to the perforations in the spoke plane is possible in an advantageous manner, but an axial air flow between the two fan wheels which is undesirable per se is prevented due to the mutual offset of the fan wheels to the gap and the axial flow cross section thereby reduced between the inner end faces of the two fan wheels arranged axially one behind the other.

Die Erfindung sowie weitere vorteilhafte Ausgestaltungen der Erfindung werden im folgenden anhand eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels erläutert; darin zeigen:

  • FIG 1 eine axiale Draufsicht auf die Lüfterradanordnung mit zwei Lüfterrädern und einem axial mittigen Antriebsmotor;
  • FIG 2 in einem Halbbild die stirnseitige Draufsicht auf die axial äußere Stirnseite des ersten Lüfterrades;
  • FIG 3 in einem Halbbild die stirnseitige Draufsicht auf die axial äußere Stirnseite des zweiten Lüfterrades.
The invention and further advantageous embodiments of the invention are explained below with reference to an embodiment shown schematically in the drawing; show in it:
  • 1 shows an axial plan view of the fan wheel arrangement with two fan wheels and an axially central drive motor;
  • 2 shows in a field the front plan view of the axially outer end face of the first fan wheel;
  • 3 shows in a field the front plan view of the axially outer end face of the second fan wheel.

FIG 1 zeigt die axiale Draufsicht auf die Lüfterradantriebsanordnung eines für Heiz- oder Klimaanlagen von Kraftfahrzeugen vorgesehenen Radialgebläses. Auf das rechte Motorwellenende eines Kommutatormotors 1 ist ein erstes Lüfterrad 2 und auf das linke Motorwellenende des Kommutatormotors 1 ein zweites Lüfterrad 3 fest montiert. Die Motorwelle dient somit gleichzeitig als Lüfterwelle 4. Beide Lüfterräder 2 bzw.3 sind in hier nicht dargestellter, jedoch allgemein bekannter Weise von einem Spiralgehäuse als Luftführungsgehäuse umgeben. Die Ankerwicklung des dauermagneterregten Kommutatormotors 1 wird über Bürstenhalter 11,12 von einer elektrischen Zuleitung 13 gespeist.1 shows the axial top view of the fan wheel drive arrangement of a radial fan provided for heating or air conditioning systems of motor vehicles. A first fan wheel 2 is fixedly mounted on the right motor shaft end of a commutator motor 1 and a second fan wheel 3 is fixedly mounted on the left motor shaft end of the commutator motor 1. The motor shaft thus simultaneously serves as a fan shaft 4. Both fan wheels 2 and 3 are surrounded by a spiral housing as an air duct housing in a manner which is not shown here but is generally known. The armature winding of the permanent magnet-excited commutator motor 1 is fed by an electrical supply line 13 via brush holders 11, 12.

Die Figuren 2 und 3 zeigen jeweils in einem Halbbild die Draufsicht auf die jeweils axial äußere Stirnseite der Lüfterräder 2 bzw.3, die als einander identische Einheitsbauteile einstückig aus Kunststoff gespritzt sind. Jedes Lüfterrad 2,3 weist eine Nabe 26 bzw.36 zur Befestigung des Lüfterrades auf der Lüfterwelle 4, einen Lüfterschaufelkranz 21 bzw.31 sowie zur Verbindung zwischen der Nabe 4 und dem im radialen Abstand gehaltenen Lüfterschaufelkranz 21 bzw.31 vier in je einer Speichenebene S1 bzw.S2 liegende Speichen 22-25 bzw.32-35 auf, von denen in FIG 2 nur die Speichen 22,23 des rechten Lüfterrades 2 und in FIG 3 nur die Speichen 32-34 des linken Lüfterrades 3 sichtbar sind. Die Speichenebenen S1 bzw.S2 jedes Lüfterrades 2 bzw.3 liegen in hinsichtlich Konstruktion und Massenausgleich günstiger Weise axial mittig zwischen den Stirnseiten ihrer Lüfterräder. Zwischen den Speichen 22-25 bzw.32-35 sind Durchbrechungen in den Speichenebenen S1 bzw.S2 vorgesehen, derart daß ein axialer Luftführungsausgleich der an beiden Stirnseiten jedes Lüfterrades eintretenden Luftströme im Sinne einer gleichmäßigen vollen Beaufschlagung der Austrittsseite des Lüfterrades trotz des gegebenenfalls durch den mittigen Antriebsmotor behinderten Lufteintritts an den dem Antriebsmotor 1 zugewandten inneren Stirnseiten jedes Lüfterrades 2 bzw.3 erfolgen kann.FIGS. 2 and 3 each show a top view of the respective axially outer end face of the fan wheels 2 and 3, which are injection-molded in one piece from plastic as identical unit components. Each Fan wheel 2, 3 has a hub 26 or 36 for fastening the fan wheel on the fan shaft 4, a fan blade ring 21 or 31 and for connection between the hub 4 and the fan blade ring 21 or 31, which are held at a radial distance, four each in a spoke plane S1 or S2 lying spokes 22-25 or 32-35, of which only the spokes 22, 23 of the right fan wheel 2 are visible in FIG. 2 and only the spokes 32-34 of the left fan wheel 3 are visible in FIG. The spoke planes S1 and S2 of each fan wheel 2 and 3 are located axially centrally between the end faces of their fan wheels in terms of construction and mass balance. Openings are provided in the spoke planes S1 and S2 between the spokes 22-25 and 32-35, respectively, so that an axial air flow compensation of the air flows entering on both end faces of each fan wheel in the sense of a uniform full loading of the outlet side of the fan wheel despite the possibly by the central drive motor impeded air entry can take place on the inner end faces of the drive motor 1 facing each fan wheel 2 or 3.

Erfindungsgemäß sind die beiden als Einheitsbauteil ausgeführten einander identischen Lüfterräder 2 bzw.3 auf der gemeinsamen Lüfterwelle 4 derart befestigt, daß sie, in Achsrichtung gesehen, um den Verdrehungs-Umfangswinkel gegeneinander auf Lücke versetzt angeordnet sind. Bei der hier vorgesehenen Verteilung von vier Speichen 22-25 bzw. 32-35 über den Umfang der Speichenebenen S1 bzw.S2 beträgt somit der Verdrehungs-Umfangswinkel      = 45°. According to the invention, the two identical fan wheels 2 and 3, designed as a unit component, are fastened on the common fan shaft 4 in such a way that, viewed in the axial direction, they are offset from one another by a gap by the circumferential angle of rotation. With the distribution of four spokes 22-25 and 32-35 provided here over the circumference of the spoke planes S1 and S2, the circumferential angle of rotation = 45 °.

Claims (7)

1. Radialventilator mit zwei axial mittelbar bzw. unmittelbar hintereinander auf einer Welle angeordneten Lüfterrädern mit jeweils über Speichen unter Freilassung von tangentialen Zwischenräumen mit in radialem Abstand zu einer auf der Lüfterwelle befestigten Lüfterradnabe gehaltenem Lüfterschaufelkranz, dadurch gekennzeichnet, daß in Achsrichtung (Lüfterwelle 4) gesehen die Speichen (22-25) des einen Lüfterrades (2) relativ zu den Speichen (32-35) des anderen Lüfterrades (3) auf Lücke (Verdrehungs-Umfangswinkel ) in Umfangsrichtung gegeneinander versetzt angeordnet sind.1. Centrifugal fan with two axially indirectly or immediately one behind the other on a shaft arranged fan wheels each with spokes leaving tangential gaps with a radial distance from a fan wheel hub attached to the fan shaft hub, characterized in that seen in the axial direction (fan shaft 4) the spokes (22-25) of one fan wheel (2) are offset relative to the spokes (32-35) of the other fan wheel (3) at a gap (circumferential angle of rotation) in the circumferential direction. 2. Radialventilator nach Anspruch 1, gekennzeichnet durch lediglich nur je eine, insbesondere radial mittige, Speichenebene (S1 bzw.S2) für jedes Lüfterrad (2 bzw.3).2. Centrifugal fan according to claim 1, characterized by only one, in particular radially central, spoke plane (S1 or S2) for each fan wheel (2 or 3). 3. Radialventilator nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß in Achsrichtung gesehen, die Speichen (22-25) des einen Lüfterrades (2) genau mittig auf Lücke gegenüber den Speichen (32-35) des anderen Lüfterrades (3) angeordnet sind.3. Centrifugal fan according to claim 1 and / or 2, characterized in that seen in the axial direction, the spokes (22-25) of a fan wheel (2) exactly in the middle of the gap with respect to the spokes (32-35) of the other fan wheel (3) are arranged. 4. Radialventilatoren nach einem der Ansprüche 1 - 3, gekennzeichnet durch vier, um den Umfangswinkel 90° je Speichenebene (S1 bzw.S2) gegeneinander versetzt angeordnete Speichen (22-25 bzw.32-35).4. Centrifugal fans according to one of claims 1-3, characterized by four spokes (22-25 or 32-35) arranged offset with respect to one another by the circumferential angle 90 ° per spoke plane (S1 or S2). 5. Radialventilatoren nach einem der Ansprüche 1 - 4, gekennzeichnet durch jeweils einander identische, jedoch um den Verdrehungs-Umfangswinkel gegeneinander versetzt auf der Lüfterwelle (4) befestigte Lüfterräder (2 bzw.3).5. Radial fans according to one of claims 1-4, characterized by identical to each other, but offset by the circumferential angle of rotation relative to each other on the fan shaft (4) attached fan wheels (2 and 3). 6. Radialventilator mit einem gemeinsamen Antriebsmotor für beide Lüfterräder nach einem der Ansprüche 1 - 4, dadurch gekennzeichnet, daß das eine Lüfterrad (2) auf dem einen Wellenende und das andere Lüfterrad (3) um den Verdrehungs-Umfangswinkel versetzt auf dem anderen Wellenende der Lüfterwelle (4) des gemeinsamen Antriebsmotors (1) befestigt sind.6. Centrifugal fan with a common drive motor for both fan wheels according to one of claims 1-4, characterized in that the one fan wheel (2) on one shaft end and the other fan wheel (3) offset by the circumferential angle of rotation on the other shaft end Fan shaft (4) of the common drive motor (1) are attached. 7. Radialventilator nach Anspruch 6, gekennzeichnet durch ein je Lüfterrad (2 bzw.3) eigenes umgebendes Luftführungsgehäuse, insbesondere Spiralgehäuse, mit Lufteintrittsöffnungen auch in den antriebsmotorseitigen Stirnseiten der Luftführungsgehäuse.7. Radial fan according to claim 6, characterized by a respective fan wheel (2 or 3) own surrounding air duct housing, in particular spiral housing, with air inlet openings in the drive motor end faces of the air duct housing.
EP87113062A 1986-09-19 1987-09-07 Radial fan Revoked EP0261490B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863631942 DE3631942A1 (en) 1986-09-19 1986-09-19 RADIAL FAN
DE3631942 1986-09-19

Publications (2)

Publication Number Publication Date
EP0261490A1 true EP0261490A1 (en) 1988-03-30
EP0261490B1 EP0261490B1 (en) 1990-03-21

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EP87113062A Revoked EP0261490B1 (en) 1986-09-19 1987-09-07 Radial fan

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US (1) US4746266A (en)
EP (1) EP0261490B1 (en)
DE (2) DE3631942A1 (en)

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EP1701101A2 (en) * 2005-02-15 2006-09-13 Lg Electronics Inc. Ventilating system
CN107288923A (en) * 2017-07-13 2017-10-24 广东美的厨房电器制造有限公司 Lampblack absorber impeller and lampblack absorber

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US5388956A (en) * 1994-03-09 1995-02-14 General Electric Company Fan assembly and method for reducing fan noise
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FI101565B1 (en) 1997-01-17 1998-07-15 Flaekt Oy Evaporation fan and its impeller
DE10002951C1 (en) * 2000-01-25 2000-11-30 Daimler Chrysler Ag Radial ventilation fan for automobile passenger compartment has 2 separate fan stages driven by central electric motor contained within respective ventialtion channels leading to floor of passenger compartment
US6896478B2 (en) * 2002-12-16 2005-05-24 Visteon Global Technologies, Inc. Dual fan blower with axial expansion
CN1295438C (en) * 2003-09-15 2007-01-17 海尔集团公司 Blower fan with single electric machine and bilobed wheel
ITBO20070382A1 (en) * 2007-05-31 2008-12-01 Spal Automotive Srl ELECTRIC
CN105179311A (en) * 2015-09-01 2015-12-23 吉首大学 Dust-deposition-preventing long-shaft fan impeller with wedge-shaped blade

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EP1701101A3 (en) * 2005-02-15 2007-10-24 Lg Electronics Inc. Ventilating system
US7575044B2 (en) 2005-02-15 2009-08-18 Lg Electronics Inc. Ventilating system
CN107288923A (en) * 2017-07-13 2017-10-24 广东美的厨房电器制造有限公司 Lampblack absorber impeller and lampblack absorber

Also Published As

Publication number Publication date
DE3761995D1 (en) 1990-04-26
US4746266A (en) 1988-05-24
DE3631942A1 (en) 1988-04-07
DE3631942C2 (en) 1988-06-30
EP0261490B1 (en) 1990-03-21

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