EP1703139B1 - Centrifugal ventilator - Google Patents

Centrifugal ventilator Download PDF

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Publication number
EP1703139B1
EP1703139B1 EP20060004223 EP06004223A EP1703139B1 EP 1703139 B1 EP1703139 B1 EP 1703139B1 EP 20060004223 EP20060004223 EP 20060004223 EP 06004223 A EP06004223 A EP 06004223A EP 1703139 B1 EP1703139 B1 EP 1703139B1
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EP
European Patent Office
Prior art keywords
characterized
radial fan
fan according
casing
part
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EP20060004223
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German (de)
French (fr)
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EP1703139A1 (en
Inventor
Rudolf Tungl
Roland Keber
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Ebm Papst Landshut GmbH
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Ebm Papst Landshut GmbH
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Priority to DE200520004180 priority Critical patent/DE202005004180U1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44Fluid-guiding means, e.g. diffusers
    • F04D29/441Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422Discharge tongues

Description

  • Die Erfindung betrifft ein Radialgebläse mit einem ein Seitenteil und ein topfartiges Gehäuseteil aufweisenden Gehäuse und einem in dem Gehäuse angeordneten Lüfterrad, mit sich radial erstreckenden Schaufeln. The invention relates to a radial fan with a one side part and a pot-like housing part comprising a housing and a cylinder disposed in the housing impeller with radially extending blades.
  • Derartige Vorrichtungen zum Fördern von gasförmigen Medien werden in der Regel eingesetzt in Vorrichtungen, die einen großen Strömungswiderstand besitzen. Such devices for conveying gaseous media are usually used in devices that have a high flow resistance. Es kann sich dabei um keramische Flächenbrenner handeln, die in der neuesten Entwicklung in Gaskesseln verwendet werden. They may be doing to ceramic surface burner used in the latest development in gas boilers. Derartige Gasheizkessel weisen einen Strömungswiderstand in der Größenordnung von 200 Paskal und mehr auf. Such gas boilers have a flow resistance in the order of 200 Paskal and more. Zur Überwindung des großen Strömungswiderstands ist man bestrebt, möglichst steile Druckvolumen-Stromkennlinien bei einem Radialgebläse zu erzeugen. To overcome the large flow resistance, the aim is to produce as steep as possible pressure volume-current characteristics in a radial blower.
  • Radialgebläse der genannten Gattung sind im Stand der Technik bekannt. Radial fan of the above type are known in the art. So ist in der Thus in the EP 0 410 271 A2 EP 0410271 A2 eine Vorrichtung zum Fördern eines gasförmigen Mediums bekannt, bei dem das Gehäuseteil eine Halterung für den Elektromotor aufweist und das Seitenteil mit einer Einlassöffnung für den Zustrom der Gebläseluft versehen ist. a device for conveying a gaseous medium, in which the housing part has a holder for the electric motor and the side part is provided with an inlet opening for the inflow of the blast air.
  • Die Druckschrift The publication US 2004/0062646 A1 US 2004/0062646 A1 , die als nächstliegenden Stand der Technik angesehen wird, offenbart die Merkmale des Oberbegriffs des Anspruchs 1. , Which is regarded as closest prior art, discloses the features of the preamble of claim 1.
  • Der Erfindung liegt die Aufgabe zugrunde, ein Radialgebläse anzugeben, das bei möglichst gleicher Leistung besonders raumsparend, kostengünstig und einfach herzustellen ist. The invention has for its object to provide a centrifugal blower which is particularly space-saving, inexpensive and easy to manufacture at the same power as possible.
  • Die Aufgabe wird bei einem Gebläse der genannten Gattung durch die im Anspruch 1 angegebenen Merkmale gelöst. The object is achieved by the features specified in claim 1. wherein a fan of the aforementioned type.
  • Die erfindungsgemäße Lösung sieht daher vor, ein Radialgebläse mit einem ein Seitenteil und ein topfartiges Gehäuseteil aufweisendes Gehäuse zu schaffen, mit einem darin angeordneten Lüfterrad, einem am Seitenteil angeordneten Elektromotor und mit einem von Gehäuseteil und Seitenteil gebildeten Druckraum, der mit dem Lüfterrad-Raum zwischen den Schaufeln im Querschnitt eine Düse nach Art einer Venturi-Düse bildet, wobei das Verhältnis größte Schaufelhöhe (H) / größter Durchmesser (D) der Spirale im Wesentlichen zwischen H/D = 0,08 und H/D = 0,3 beträgt. The solution according to the invention therefore provides to provide a centrifugal blower with a one side part and a pot-like housing part housing having, having disposed therein impeller, arranged on the side part electric motor and with a space formed by housing part and side part of the pressure chamber located between the impeller room forming the vanes in cross-section a nozzle of a venturi nozzle, wherein the ratio of largest blade height (H) / largest diameter (D) of the spiral substantially between H / D = 0.08 and H / D = 0.3. Durch die besondere Gestaltung der Druckraumgeometrie und der Auslegung der Schaufeln des Lüfterrads im Verhältnis zum Durchmesser der Spirale des Druckraums, werden die gewünschten Leistungen in hervorragender Weise erreicht. The special design of the pressure chamber geometry and the design of the blades of the fan relative to the diameter of the spiral of the pressure chamber, the desired performance is achieved in an excellent manner. Vorzugsweise beträgt das Verhältnis H/D = 0,1, besonders bevorzugt beträgt jedoch das Verhältnis H/D = 0,12. Preferably, the ratio H / D = 0.1, but more preferably, the ratio H / D = 0.12. Dies entspricht bei einer konstruktiven Ausgestaltung einem größten Durchmesser von ca. 145,3 mm bei einer Schaufelhöhe von 18 mm. This corresponds to a structural configuration of a maximum diameter of about 145.3 mm with a blade height of 18 mm.
  • Besonders vorteilhaft ist es, wenn im Gehäuseteil und/oder im Seitenteil Ausformungen ausgebildet sind, durch die sich der spiralenförmige Druckraum kontinuierlich dreidimensional erweitert. It is particularly advantageous when protrusions are formed in the housing part and / or in the side part, the spiral-shaped pressure chamber extends continuously in three dimensions through which.
  • Vorzugsweise ist die Ausformung im Gehäuseteil größer als im Seitenteil. Preferably, the formation in the housing part is greater than in the side part. Durch die Wahl der Gehäusegestalt und die Anordnung der größeren Ausformung im Gehäuseteil ergibt sich die Möglichkeit, auf der dem Motor abgewandten Seite des GebläseGehäuses in gewünschter Weise Ausformungen anzubringen, ohne dass eine räumliche Einschränkung gegeben wäre. By choosing the housing shape and the arrangement of the larger formation in the housing part there is the possibility, on the opposite side to the motor of the fan housing to attach formations in the desired manner without any spatial restriction would be given.
  • Günstigerweise wird das Verhältnis Höhe/Durchmesser des Gehäuses zwischen 1:7 und 1:9 gewählt. Conveniently, the ratio height / diameter of the casing is between 1: 9 selected: 7 and the first Besonders vorteilhaft ist es, wenn das Verhältnis Höhe/Durchmesser des Gehäuses 1:8 beträgt. It is particularly advantageous when the ratio / diameter of the housing 1 height: 8.
  • Besonders vorteilhaft ist es, wenn bei einer Drehzahl von n = 5250 ein Luftvolumenstrom von 11 L/s geliefert wird. It is particularly advantageous when an air flow rate of 11 L / s is delivered at a speed of n = 5250 is. Dabei ergibt sich eine Luftleistungskennzahl von pa = 1050 (Druck), der bei einer Drehzahl von 5250 und dem genannten Luftvolumenstrom von 11 L/s eine Wellenleistung von ca. 21 W erfordert. In this case, an air coefficient of performance results of pa = 1050 (pressure) at a speed of 5250 and the air volume flow of 11 L / s requires a shaft output of about 21 W above. Dies ist im Vergleich zum Stand der Technik ein sehr niedriger Wert. This is a very low value compared to the prior art.
  • Eine weitere vorteilhafte Ausgestaltung ist darin zu sehen, dass die Ebene des Anschlusses am Ausblaskanal des Gehäuses in einem Winkel α≤90° zur Ausblasrichtung (Pfeil A) steht. Another advantageous embodiment is seen therein that the plane of the terminal on the outlet duct of the housing is at an angle α≤90 ° to the discharge direction (arrow A). Besonders vorteilhaft ist es, wenn der Winkel zwischen 90° und 83° liegt, wobei besonders bevorzugt α = 86,4° beträgt. It is particularly advantageous if the angle between 90 ° and 83 °, wherein particularly preferably α = 86.4 °.
  • Eine günstige Ausführungsform kann vorsehen, dass der Ausblaskanal am Gehäuseteil ausgebildet ist. A favorable embodiment may provide that the blow-out channel is formed on the housing part.
  • Von besonderem Vorteil ist, dass das Gehäuse eine in den Druckraum hinein ragende Zunge aufweist. Is that the housing has a projecting into the pressure chamber tongue of particular advantage. Dabei ist es günstig, dass die Zunge am Gehäuseteil in Form einer Rampe ausgebildet ist, die auf der Seitenwand des Gehäuseteils in Strömungsrichtung ansteigt. It is favorable that the tongue is in the form of a ramp on the housing part, which rises on the side wall of the housing part in flow direction. Durch die Anbringung einer Zunge wird der Druckraum im Ausblasbereich gegen das Lüfterrad abgeschirmt, so dass Druckverluste reduziert werden können. By mounting a tongue of the pressure chamber is shielded in the blow against the impeller so that pressure losses can be reduced.
  • Bei einer anderen Ausführungsform kann es vorteilhaft sein, dass die Zunge am Seitenteil in Form einer Rampe ausgebildet ist und in Strömungsrichtung zum Gehäuseteil hin ansteigt. In another embodiment, it may be advantageous that the tongue on the side part is in the form of a ramp and increases in the flow direction to the housing part. Durch die Ausbildung der Zunge als Rampe kann der Spalt zwischen Lüfterrad und Seitenwand des Gehäuseteils verringert werden, ohne dass es zu einem Ansteigen des Geräuschpegels kommt. By making the tongue as a ramp, the gap between the fan wheel and the side wall of the housing part can be reduced without causing an increase in the noise level.
  • Bei einer weiteren Ausführungsform des Gebläses kann vorgesehen sein, ein Lüfterrad mit einer Nabe und einer vorderen Deckscheibe zu verwenden, wobei dann die Schaufeln des Lüfterrads lediglich an der Nabe und der Deckscheibe gehalten sind. In another embodiment of the fan, a fan wheel can be used with a hub and a front cover plate may be provided, in which case the blades of the impeller are supported only on the hub and the shroud. Eine rückwärtige Trägerscheibe kann entfallen. A rear carrier disc can be omitted. Hierdurch ergibt sich eine kostengünstige Herstellung des Lüfterrads und somit des Radialgebläses insgesamt. This results in a cost-effective production of the fan wheel and thus the overall radial fan.
  • Im Folgenden wird die Erfindung anhand in der Zeichnung dargestellter Ausführungsbeispiele näher erläutert. In the following the invention is explained in more detail with reference shown in the drawings embodiments. Es zeigen: Show it:
  • Fig. 1 Fig. 1
    eine Seitenansicht eines Radialgebläses, a side view of a radial fan,
    Fig. 2 Fig. 2
    eine Forderansicht auf das Radialgebläse mit Motor und Anschlussflansch, a Forderansicht on the radial fan with motor and connecting flange,
    Fig. 3 Fig. 3
    eine schematische Darstellung mit Druckraum, und a schematic illustration of the pressure chamber, and
    Fig. 4 Fig. 4
    eine schematische Darstellung der Zuordung Lüfterrad-Raum - Druckraum im Schnitt. a schematic representation of the assignment fan room - pressure chamber in section.
  • In In Fig. 1 Fig. 1 ist ein Radialgebläse in Seitenansicht dargestellt, das ein Gehäuse 4 aufweist, in dem ein Lüfterrad 5 aufgenommen ist. a radial fan in a side view is shown, which comprises a housing 4 in which a fan 5 is added. Das Gehäuse 4 besteht aus einem Seitenteil 2 und einem topfartigen Gehäuseteil 3. An dem Seitenteil 2 ist ein Elektromotor 7 schwingungsgedämpft gehalten, der über seine Motorwelle das Lüfterrad 5 antreibt. The housing 4 is composed of a side part 2 and a pot-shaped housing part 3. On the side part 2 is an electric motor 7 is held vibration damped, which drives the impeller 5 via its motor shaft. Das Gehäuse weist einen, in Verbindung mit The housing has a, in conjunction with Fig. 3 Fig. 3 näher beschriebenen Druckraum 8 auf. Pressure chamber in more detail above 8. Das Lüfterrad 5 bildet zusammen mit dem Druckraum 8, wie ebenfalls in The fan 5 together with the pressure chamber 8, as also shown in Fig. 3 Fig. 3 näher erläutert, eine idealisierte Venturi-Düse, wobei der engste Querschnitt dieser Venturi-Düse im Übergang zwischen Lüfterrad und Gehäuse liegt. explained in more detail, an idealized Venturi nozzle, the narrowest cross-section of said venturi nozzle is located in the transition between the impeller and the housing.
  • Im Gehäuseteil 3 und/oder im Seitenteil 2 sind Ausformungen 19 ausgebildet, durch die sich der spiralenförmige Druckraum 8 kontinuierlich dreidimensional erweitert. In the housing part 3 and / or in the side part 2 formations 19 are formed, the spiral-shaped pressure chamber 8 extends continuously through the three-dimensionally.
  • Die Ausformung 19 ist im dargestellten Ausführungsbeispiel im Gehäuseteil 3 größer als im Seitenteil 2. The formation 19 is greater than in the side part 2 in the illustrated embodiment in the housing part. 3
  • In In Fig. 2 Fig. 2 ist eine Forderansicht des Radialgebläses dargestellt. a Forderansicht of the radial fan is shown. Das Gebläse einen Ausblaskanal 13 und eine Ansaugöffnung 20 auf. The fan a fan outlet duct 13 and a suction port 20. Wie in der Ansaugöffnung zu erkennen ist, handelt es sich bei dem dargestellten Ausführungsbeispiel um ein Lüfterrad mit rückwärts gekrümmten Schaufeln. As can be seen in the intake port, it is in the illustrated embodiment, a fan impeller with backward curved blades. Am freien Ende des Ausblaskänals 13 ist ein Anschluss 12 in Form eines Flansches 12 vorgesehen. At the free end of the Ausblaskänals 13, a port is provided in the form of a flange 12 12th Die Ebene 11 des Anschlusses 12 bildet im dargestellten Ausführungsbeispiel mit der theoretischen Ausblasrichtung - Pfeil A - einen Winkel α ≤ 90°. The plane 11 of the terminal 12 forms in the illustrated embodiment with the theoretical discharge direction - arrow A - an angle α ≤ 90 °. In einer besonders bevorzugten Ausführungsform beträgt der Winkel α = 86,4°. In a particularly preferred embodiment, the angle α = 86.4 °. Durch diese Anordnung wird der austretende Luftstrom noch weiter druckvermindernd geführt, da durch die winkelmäßige Anordnung zwischen Kanalfortsetzung und Ausblaskanal die Spiralkontur des Gebläses fortgesetzt wird. By this arrangement, the exiting air flow is further led druckvermindernd because the spiral contour of the blower is continued by the angular arrangement between the channel extension and the exhaust chimney. Hiermit geht gleichzeitig eine Druckerhöhung einher. This is simultaneously accompanied by an increase in pressure. In der zeichnerischen Darstellung laufen die theoretische Ausblasrichtung - Pfeil A - und die Seitenwand 16 des Kanals - durch zwei Parallelstriche gekennzeichnet - parallel zueinander. Arrow A - - and the side wall 16 of the channel - in the graphic representation of the theoretical air discharge run characterized by two parallel strokes - parallel to each other. Ebenso - verlaufen die senkrechte Mittelachse des Gebläses und die Ebene 11 parallel zueinander. Likewise - extending the vertical center axis of the fan and the plane 11 parallel to each other.
  • In In Fig. 3 Fig. 3 ist schematisch das Gebläse-Gehäuse 4 dargestellt, in dem das Lüfterrad 5 eingesetzt ist. is schematically shown the fan housing 4, in which the fan wheel 5 is inserted. Der spiralförmige Druckraum wird im Bereich des Ausblaskanals 13 durch die Zunge 14 gegen das Lüfterrad 5 abgeschirmt. The spiral-shaped pressure chamber is shielded in the area of ​​the blow-out channel 13 through the tongue 14 against the fan impeller. 5 In dieser Darstellung ist mit β = 3,6° der Komplementärwinkel zu dem Winkel α eingezeichnet. In this illustration, the complementary angle 3.6 ° is located α to the angle β = with.
  • Erfindungsgemäß beträgt das Verhältnis H (größte Schaufelhöhe) zu D (Durchmesser der Spirale) im dargestellten Ausführungsbeispiel 0,12. According to the invention, the ratio H is (largest blade height) to D (diameter of the coil) in the illustrated embodiment 0.12. Es hat sich während Testserien herausgestellt, dass Abweichungen von diesem Verhältnis noch brauchbare Ergebnisse liefern, jedoch ist der Wert 0,12 bei einem Spiraldurchmesser von 145,3 mm und einer geforderten Volumenstromkennzahl von 11 I/s das optimale Maß. It has been found during test series, that deviations from this ratio still deliver useful results, but the value is 0.12 with a spiral diameter of 145.3 mm and a required volume flow index of from 11 I / s, the optimum degree. Diese Leistung wird erreicht bei einer Drehzahl von 5250 U/min und einer Wellenleistung von 21 W. This performance is achieved at a speed of 5250 rev / min and a shaft power of 21 W.
  • In In Fig. 4 Fig. 4 ist schematisch das Venturi-Düsen-Prinzip wiedergegeben, wobei der Bereich 9 als Lüfterrad-Raum zusätzlich zur Drehzahl des Lüfterrads durch die konstruktive Gestaltung, eine weitere Beschleunigung des Luftstroms bewirkt, wohingegen der Druckraum 8 die Druckerhöhung und Beruhigung des Luftstroms herbeiführt. schematically the venturi principle reproduced, the region 9 as a fan room in addition to the rotational speed of the impeller by the design, causes a further acceleration of the air flow, whereas the pressure chamber 8, brings the pressure-increasing and calming the air flow.
  • Bei der in den Figuren dargestellten Ausführungsform ist, wie schematisch in in the illustrated embodiment in the drawings, as shown schematically in Fig. 4 Fig. 4 wiedergegeben, das Lüfterrad 5 mit einer Nabe 17 versehen, wobei die Schaufeln 6 an der Nabe 17 und an einer Deckscheibe 18 gehalten sind. reproduced, the fan 5 is provided with a hub 17, the blades being held on the hub 17 and a cover plate 18. 6 Es versteht sich, dass entsprechend gewünschter Leistungsanforderungen auch andere Lüfterräder Verwendung finden können. It is understood that can also find other fan wheels used in accordance with the desired performance requirements.
  • Bezugszeichenliste: LIST OF REFERENCE NUMBERS
  • 1 1
    Radialgebläse centrifugal blower
    2 2
    Seitenteil side panel
    3 3
    topfartiges Gehäuseteil pot-shaped housing part
    4 4
    Gehäuse casing
    5 5
    Lüfterrad fan
    6 6
    Schaufeln shovel
    7 7
    Elektromotor electric motor
    8 8th
    Druckraum pressure chamber
    9 9
    Lüfterrad-Raum Fan room
    10 10
    Düse jet
    11 11
    Ebene des Anschlusses 12 Level of the terminal 12
    12 12
    Anschluss connection
    13 13
    Ausblaskanal blow-out
    Pfeil A arrow A
    Ausblasrichtung Discharge
    14 14
    Zunge tongue
    15 15
    Rampe ramp
    16 16
    Seitenwand des Gehäuseteils 3 Side wall of the housing part 3
    17 17
    Nabe hub
    18 18
    Deckscheibe cover disc

Claims (16)

  1. A radial fan (1) comprising a casing (4) having a side part (2) and a pot-shaped casing part (3), a fan wheel (5) arranged inside the casing and having radially extending blades (6), an electric motor (7) arranged at the side part, and a compression space (8) formed by the casing part and the side part, characterized in that the compression space together with the fan wheel space between the blades (6) in its cross-section forms a nozzle (8') of a Venturi nozzle type, and that the relation largest blade height (H)/largest diameter (D) of the spiral substantially is in the range between H/D = 0.08 and H/D = 0.3.
  2. The radial fan according to claim 1, characterized in that the relation largest blade height (H)/largest diameter (D) of the spiral preferably is substantially H/D = 0.1, particularly preferred H/D = 0.12.
  3. The radial fan according to claim 1 or 2, characterized in that recesses (19) are formed in the casing part (3) and/or the side part (2) by means of which the spiral-shaped compression space (8) is continuously enlarged in a three-dimensional manner.
  4. The radial fan according to claim 3, characterized in that the recess (19) in the casing part (3) is larger than in the side part (2).
  5. The radial fan according to one of the preceding claims, characterized in that the relation height/diameter of the casing (4) is between 1:7 and 1:9.
  6. The radial fan according to claim 5, characterized in that the relation height/diameter of the casing (4) is substantially 1:8.
  7. The radial fan according to one of the preceding claims, characterized in that an air volume flow of about 11 l/s is delivered at a speed of about n = 5250.
  8. The radial fan according to one of the preceding claims, characterized in that the performance characteristics l/s = 11 (volume flow) and Pa = 1050 (pressure) are obtained at a speed of n = 5250 and a shaft output of about 21 W.
  9. The radial fan according to one of the preceding claims, characterized in that the plane (11) of the connecting portion (12) at the exhaust passage (13) of the casing (4) is arranged at an angle α ≤ 90° to the exhaust direction (arrow A).
  10. The radial fan according to claim 9, characterized in that the plane of the connecting portion (12) at the exhaust passage (13) of the casing (4) is arranged at an angle of 90° > α ≥ 83°, preferably α = 86.4° to the exhaust direction (arrow A).
  11. The radial fan according to one of the preceding claims, characterized in that the exhaust passage (13) is formed in the casing part (3).
  12. The radial fan according to one of the preceding claims, characterized in that the casing (4) comprises a tab (14) projecting into the compression space (8).
  13. The radial fan according to claim 12, characterized in that the tab (14) on the casing part (3) is in the form of a ramp (15) rising in the direction of flow on the side wall (16) of the casing part (3).
  14. The radial fan according to claim 12, characterized in that the tab (14) is formed on the side part (2) in the form of a ramp (15) which rises in the direction of flow towards the casing part (3).
  15. The radial fan according to at least one of the preceding claims, characterized in that the fan wheel (5) comprises a hub (17) and at least one cover disc (18).
  16. The radial fan according to claim 15, characterized in that only one cover disc (18) is provided at the fan wheel (5) and that the blades (8) are supported only on the hub (17) and the single cover disc (8).
EP20060004223 2005-03-14 2006-03-02 Centrifugal ventilator Active EP1703139B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE200520004180 DE202005004180U1 (en) 2005-03-14 2005-03-14 centrifugal blower

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EP1703139A1 EP1703139A1 (en) 2006-09-20
EP1703139B1 true EP1703139B1 (en) 2011-01-26

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US (1) US8257034B2 (en)
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AT (1) AT497109T (en)
DE (2) DE202005004180U1 (en)
ES (1) ES2360580T3 (en)

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US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device

Families Citing this family (6)

* Cited by examiner, † Cited by third party
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CN102834621B (en) 2010-04-06 2015-11-25 3M创新有限公司 Radial blower having a volute shaped profile
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
EP3139046A3 (en) * 2015-09-07 2017-08-09 E.M.C. S.r.l. Electric centrifugal blower

Family Cites Families (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3093299A (en) * 1961-05-15 1963-06-11 Trane Co Centrifugal fan
US3824028A (en) * 1968-11-07 1974-07-16 Punker Gmbh Radial blower, especially for oil burners
ES461142A1 (en) * 1976-09-04 1978-06-01 Mtu Friedrichshafen Gmbh Improvements in turbo-chargers exhaust gas combustion engines.
US4381171A (en) * 1978-10-20 1983-04-26 Cummins Engine Company, Inc. Casting for a turbine wheel
GB2057567A (en) * 1979-08-24 1981-04-01 Borg Warner Expanding scroll diffuser for radial flow impeller
DE3001868C2 (en) * 1980-01-19 1984-01-19 Klein, Schanzlin & Becker Ag, 6710 Frankenthal, De
DE3005094C2 (en) * 1980-02-12 1983-02-24 Klein, Schanzlin & Becker Ag, 6710 Frankenthal, De
JPS648199B2 (en) * 1983-12-29 1989-02-13 Matsushita Electric Ind Co Ltd
US4785515A (en) * 1986-07-09 1988-11-22 Willette Russell J Method of making a centrifugal pump
US5133642A (en) * 1988-02-29 1992-07-28 Ebara Corporation Pipe joint for pump
DE69003955T2 (en) * 1989-01-19 1994-02-17 Ebara Corp Pump housing.
WO1990009524A1 (en) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Centrifugal fan and diffuser with accumulating volute
CA1331872C (en) * 1989-05-23 1994-09-06 Richard Sixsmith Centrifugal radially aligned outlet type fan with baffle
DE3924281A1 (en) * 1989-07-22 1991-01-31 Standard Elektrik Lorenz Ag Apparatus for conveying a houses on gaseous medium
DE4009869A1 (en) * 1990-03-28 1991-10-02 Mulfingen Elektrobau Ebm Radialgeblaese with internal spiral
US5156524A (en) * 1990-10-26 1992-10-20 Airflow Research And Manufacturing Corporation Centrifugal fan with accumulating volute
US5281092A (en) * 1991-01-18 1994-01-25 Sullivan John T Volute housing for a centrifugal fan, blower or the like
US5141397A (en) * 1991-01-18 1992-08-25 Sullivan John T Volute housing for a centrifugal fan, blower or the like
CA2127793A1 (en) * 1992-01-13 1993-07-22 William Stuart Gatley, Jr. Noise cancellation device for centrifugal blower
US5324167A (en) * 1993-08-20 1994-06-28 Tlt-Babcock, Inc. Centrifugal fan
US5551836A (en) * 1995-01-27 1996-09-03 Revcor, Inc. High pressure combustion blower assembly
JPH09242696A (en) * 1996-03-11 1997-09-16 Denso Corp Centrifugal blower
TW381150B (en) * 1996-03-29 2000-02-01 Sanyo Electric Co Electric fan
CA2229127C (en) * 1997-03-03 2001-06-12 William J. Roy Method of venting a furnace
DE19740590A1 (en) * 1997-09-15 1999-03-18 Klein Schanzlin & Becker Ag Volute casing pump
US6299409B1 (en) * 1998-04-10 2001-10-09 Denso Corporation Centrifugal type blower unit
EP0961087B1 (en) * 1998-05-26 2004-11-24 Carrier Corporation Fan scroll
US6146092A (en) * 1998-07-13 2000-11-14 Ford Motor Company Centrifugal blower assembly with a diffuser
US6056506A (en) * 1998-09-23 2000-05-02 Emerson Electric Co. Pump assembly for jetted tub
US6224335B1 (en) * 1999-08-27 2001-05-01 Delphi Technologies, Inc. Automotive air conditioning fan assembly
JP4185654B2 (en) * 2000-08-04 2008-11-26 カルソニックカンセイ株式会社 Centrifugal multi-blade fan
US6314894B1 (en) * 2000-08-30 2001-11-13 Jakel Incorporated Furnace blower housing with integrally formed exhaust transition
US6575696B1 (en) * 2000-09-21 2003-06-10 Fasco Industries, Inc. Method of sound attenuation in centrifugal blowers
US6468034B1 (en) * 2000-12-04 2002-10-22 Fasco Industries, Inc. Flush mount round exhaust fabricated inducer housing
WO2002045862A2 (en) * 2000-12-04 2002-06-13 Robert Bosch Corporation High efficiency one-piece centrifugal blower
US20020119044A1 (en) * 2001-02-26 2002-08-29 O'connor, John F. Centrifugal blower with partitioned scroll diffuser
US20030012649A1 (en) * 2001-07-16 2003-01-16 Masaharu Sakai Centrifugal blower
US6709235B2 (en) * 2001-09-14 2004-03-23 Honeywell International Inc. Turbine housing for high exhaust temperature
US6742989B2 (en) * 2001-10-19 2004-06-01 Mitsubishi Heavy Industries, Ltd. Structures of turbine scroll and blades
JP3721346B2 (en) * 2002-06-26 2005-11-30 株式会社ケーヒン Centrifugal blower
KR100485329B1 (en) * 2002-10-09 2005-04-25 학교법인 선문학원 centrifugal blower with blade preventing eddy
AT413872B (en) * 2002-10-17 2006-06-15 Bitter Engineering & Systemtec Impeller for a pump
US6953321B2 (en) * 2002-12-31 2005-10-11 Weir Slurry Group, Inc. Centrifugal pump with configured volute
DE10313054B4 (en) * 2003-03-24 2012-10-04 Motoren Ventilatoren Landshut Gmbh centrifugal blower
US7108482B2 (en) * 2004-01-23 2006-09-19 Robert Bosch Gmbh Centrifugal blower

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring

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EP1703139A1 (en) 2006-09-20
ES2360580T3 (en) 2011-06-07
DE502006008789D1 (en) 2011-03-10
US20060204382A1 (en) 2006-09-14
AT497109T (en) 2011-02-15
US8257034B2 (en) 2012-09-04

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