EP2196679B1 - Impeller for a radial fan - Google Patents

Impeller for a radial fan Download PDF

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Publication number
EP2196679B1
EP2196679B1 EP10157619.7A EP10157619A EP2196679B1 EP 2196679 B1 EP2196679 B1 EP 2196679B1 EP 10157619 A EP10157619 A EP 10157619A EP 2196679 B1 EP2196679 B1 EP 2196679B1
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EP
European Patent Office
Prior art keywords
radial fan
fan impeller
blades
impeller according
disc
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EP10157619.7A
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German (de)
French (fr)
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EP2196679A2 (en
EP2196679A3 (en
Inventor
Roland Keber
Rudolf Tungl
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Ebm Papst Landshut GmbH
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Ebm Papst Landshut GmbH
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Publication of EP2196679A3 publication Critical patent/EP2196679A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/53—Building or constructing in particular ways by integrally manufacturing a component, e.g. by milling from a billet or one piece construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the present invention relates to a radial impeller, in particular for use in gas blowers with a steep fan characteristic curve.
  • the EP 0 410 271 B1 describes a radial fan for conveying a gaseous medium in a device with high flow resistance, which is in particular a burner in a gas boiler. Such burners have a relatively high flow resistance, which is of the order of 200 Pascal or more.
  • the medium to be conveyed may be air or a combustible gas-air mixture.
  • the blower or its blower wheel must therefore be designed for a steep pressure-volume flow characteristic. This means that pressure changes should be accompanied by only small changes in the volume flow.
  • the known fan has for this purpose an impeller whose diameter is more than ten times its flow outlet width.
  • first cover plate lower part
  • second cover plate circular, flat plate-shaped lid
  • the present invention has for its object to provide a Radialgebläserad, which is particularly suitable for a gas burner fan with steep curve in a simple and economical manner to produce.
  • annular cover plate which has a width R D , which is measured from the edge of the suction port is smaller than the AbstandRand- suction to discharge opening - peripheral edge.
  • the width such that it is substantially half the blade length measured from the intake opening.
  • This particular embodiment also allows a production of the impeller as a one-piece molded part, being considered as particularly favorable an embodiment in which the support disc is annular and has a ring width, which is substantially the dimension outer edge cover plate to exit opening-Umfangsrand (2-3 '. ) is.
  • this ring width is substantially half a blade length, the air flow in the exit region still a guide can be issued, so that the Scherbreibung between the rear housing wall and the flow is limited to a reduced range.
  • the two disc rings namely that of the cover disc and that of the support disc, either overlap in the projection in the direction of the axis of rotation as required, form a gap between them or subsequently complement each other to form a circular area.
  • An advantageous flow course can be achieved in that the hub body has a height that corresponds to measured from the plane of the rear support plate substantially half the wheel depth.
  • a cone is formed on the hub body to the flow side, wherein the cover plate and the cone of the hub in cross-section A-A have a substantially parallel course. As a result, a favorable flow profile is achieved in the input region of the wheel.
  • a region is formed whose flow surface is substantially parallel to the plane of rotation.
  • the flow surface of the outer peripheral portion is arranged in a plane which is located with respect to the flow channel inwardly than the surface of the outer support disc defining the flow channel, d. That is, the support disk can be made thinner than the thickness of the outer peripheral portion of the cone.
  • An advantageous embodiment can be designed so that the blades are axially wider in the intake area than in the outflow area.
  • At least one intermediate blade is arranged between the blades essentially in the region of the width of the carrier disk.
  • each case two intermediate blades are arranged in pairs.
  • the intermediate blades have a radial extension which essentially corresponds to the distance between the outer circumference of the cover disk and the outer circumference of the rear support disk.
  • the intermediate blades are held exclusively on the rear support plate.
  • This embodiment particularly facilitates the formation of the radial impeller as a one-piece cast part.
  • a radial impeller 1 consists of a plurality of distributed over the circumference arranged radial blades 2, seen in the radial direction of an inner inlet region 4 to an outer outlet region 6 extend.
  • the blades 2 have radially inner end edges 8, which are located on an imaginary, approximately cylindrical, but especially conical surrounding the inlet region 4 and in the axial inflow direction (see the arrow E in FIG Fig. 1 and 4 to 6 ) seen in the inlet region 4 in the tapered surface lie.
  • the blades 2 also have outer end edges 10.
  • radial Startsmungskanäle 12 are formed with a substantially radial outflow direction A.
  • the blades 2 extend axially, ie viewed in the direction of a rotation axis 14, between an inlet side 16 and an axially opposite hub side 18 (see the sectional views in FIG 4 to 6 ).
  • the blades 2 are furthermore connected only on their inlet side 16 over their radial extent to the outlet region 6 with a cover disk 20 which has a central inlet opening 22 opening into the inlet region 4.
  • the blades are connected only with their radially inner end regions with a central hub 24, so that the flow channels 12 are formed open on this side in the axial direction.
  • the blades 2 thus have free side edges 26 on this side.
  • the blades 2 and the cover plate 20 has an outer impeller diameter D, which is at least ten times an existing in the exit region 6, axially measured flow outlet width B of the blades.
  • the axially measured inner flow inlet width C of the blades 2 in the inlet region 4 is preferably greater than the outer flow outlet width in the outlet region 6 (cf., for example, FIG Fig. 4 ).
  • a further non-inventive embodiment are with the cover plate 20 in each radially disposed between adjacent blades 2 areas intermediate blades 28 are connected (see in particular Fig. 1 and 2 ). These intermediate blades 28 extend from the outer circumference of the cover plate 20 only over part of the radial extent of the cover plate 20 and terminate at a radial distance from the hub 24. This can best be seen in Fig. 2 detect. In the illustrated embodiment, between each two adjacent blades 2 only one intermediate blade 28 is provided, but it can also be provided each two or more intermediate blades 28, which can then be designed with the same or different radial length.
  • the radial impeller 1 can be advantageously prepared as a one-piece molding made of plastic, preferably made of a plastic having such antistatic properties that during operation static charges avoided or derived via a not shown housing. This contributes to a high degree of application safety, especially with regard to the preferred application for conveying combustible gas-air mixtures, by avoiding ignition by sparking.
  • the blades 2 and the intermediate blades 28 are formed in the radial direction with respect to the direction of rotation 30 is curved backward.
  • the blades are arranged such that their entry angle is approximately between 30 ° and 45 ° and their exit angle is approximately between 45 ° and 90 °. To explain this angle is on the EP 0 410 271 Referenced.
  • an embodiment with forward curved or at the exit region 6 radially ending blades 2 and intermediate blades 28 is possible.
  • the hub 24 consists of an outer disk portion 32 and a central, to be connected to a shaft not shown bearing portion 34, in particular in the form of a short pipe socket.
  • the disc portion 32 is connected at its radially outer periphery with the inner, the inlet portion 4 facing end portions of the blades.
  • the disc portion 32 of the hub 24 is projecting from its outer peripheral region connected to the blades 2 such in the inlet region 4 and in the direction of the inflow opening 22 of the cover plate 20 projecting convexly or cup-shaped, for example, that the hub 24 -.
  • Fig. 1 please refer in particular Fig.
  • blower-functional elements such as bearing elements, motor or rotor parts and / or the like.
  • FIG. 2 shows, (at least) the intermediate blades 28 are connected to the cover plate 20 via a respective transition reinforcement 38 formed in the blade root area. This ensures, despite the connection-free, spaced from the hub 24 embodiment, a sufficient stability of the intermediate blades 28th
  • the blades 2 and the intermediate blades 28 in its radially outer and the cover plate 20 axially opposite region for mechanical reinforcement via a circumferential, integrally molded ring member 40 are connected.
  • the cover disk 20 in the region of the inflow opening 22 has a nozzle-like edge 42 in the flow direction.
  • radial impeller 2-1 has an annular cover plate 2-9, which surrounds the suction 2-7 annular. Usually, a circular suction opening 2-10 is formed on the cover plate 2-9, which is surrounded by a circumferential opening lip 2-10 '.
  • the radial impeller 2-1 further includes a hub body 2-2 and a peripheral edge 2-3.
  • the hub body 2-2 has on its side facing the suction opening 2-10 a cone 2-2 'on.
  • the impeller 2-1 is equipped with blades 2 - 6 substantially extending radially from the hub body 2 - 2 to the peripheral edge 2-3.
  • the vanes define an intake region 2-7 and an outflow region 2-8.
  • the annular cover plate 2-9 has a width R D , which measured from the edge of the suction port (2-10) is half the distance edge-outlet opening circumference 2-3.
  • the width R D thus corresponds substantially to half the blade length measured along the upper peripheral edge of the blade 2-6.
  • the foot of such a blade is integrally connected at its radially inner tip with the hub body.
  • the support disk 2-11 extending on the rear side 2-5 is annular and has at its ring a width R T which, measured from the edge of the suction opening 2-10, is substantially half of the dimension of the edge outlet opening 2-10- Peripheral edge is 2-3. This substantially corresponds to half a blade length measured along the back edge of the blade jet between peripheral edge 2-3 and bottom of the blade 2-6 on the cone 2-2 'of the hub 2-2.
  • the hub body 2-2 has a height that, measured from the plane of the rear support plate 2-11 substantially equal to half the wheel height. In the illustrated embodiment, the height of the hub corresponds to half the height of the projecting into the suction port 2-10 blades.
  • the surface F K of the cone 2-2 'of the hub 2-2 extends substantially parallel to the inner surface F D cover plate 2-9.
  • a region 2-21 is formed, the surface of which runs essentially parallel to the plane of rotation of the impeller.
  • the flow-facing surface of the cone and the rotation-parallel region are rounded.
  • intermediate blades 2-16 are arranged substantially in the region of the width of the rear support disk 2-11.
  • the number of blades 2-16 may vary depending on the application.
  • two intermediate blades 2-16 are arranged in pairs between two blades 2-6.
  • the radial extent of the intermediate blades 2-16 is dimensioned so that it substantially corresponds to the distance 2-17 between the outer periphery 2-18 of the cover plate 2-9 and the outer periphery 2-19 of the rear support plate 2-11.
  • the intermediate blades 2-16 are held exclusively on the rear support plate 2-11, that is, the front edges of the intermediate blades are free in this embodiment.
  • the intermediate blades can also be formed on the cover plate.
  • the shape of the intermediate blades corresponds in its course substantially the corresponding design of the portion of the blades 2-6 at the appropriate location.
  • the embodiment can be advantageously manufactured as a one-piece molded part made of plastic.

Abstract

The radial fan impeller (1) has a number of circumferentially distributed blades (2) which on the inlet side (16) over their radial extent to the outlet section (6) are connected to a shroud disc (20) which has a central inlet opening (22) running into the inner inlet section (4) of the impeller. Radially shorter intermediate blades (28) are connected to the shroud disc and installed in regions between adjacent blades and from the outer circumference of the shroud disc extend only over a part of the radial extent of the shroud disc and end at a radial distance from the hub (24).

Description

Die vorliegende Erfindung betrifft ein Radialgebläserad, insbesondere zum Einsatz in Gasgebläsen mit steiler Gebläse-Kennlinie.The present invention relates to a radial impeller, in particular for use in gas blowers with a steep fan characteristic curve.

Die EP 0 410 271 B1 beschreibt ein Radialgebläse zum Fördern eines gasförmigen Mediums in einer Vorrichtung mit großem Strömungswiderstand, bei der es sich insbesondere um einen Brenner in einem Gas-Heizkessel handelt. Solche Brenner weisen einen verhältnismäßig hohen Strömungswiderstand auf, der in der Größenordnung von 200 Pascal und mehr liegt, Bei dem zu fördernden Medium kann es sich um Luft oder ein brennbares Gas-Luftgemisch handeln. Das Gebläse bzw. dessen Gebläserad muss deshalb für eine steile Druck-Volumenstromkennlinie ausgelegt sein. Dies bedeutet, dass Druckänderungen mit nur geringen Änderungen des Volumenstroms einhergehen sollen. Das bekannte Gebläse weist dazu ein Gebläserad auf, dessen Durchmesser mehr als das Zehnfache seiner Strömungsaustrittsbreite beträgt. Dabei handelt es sich um ein geschlossenes, beidseitig gedeckeltes Rad mit einem im wesentlichen ebenen und eine zentrische Nabe aufweisenden Unterteil (erste Deckscheibe), einer Mehrzahl von rückwärts gekrümmten, jeweils die Form eines Kreisabschnittes aufweisenden Schaufeln und einem kreisförmigen, flach tellerförmigen Deckel (zweite Deckscheibe) mit einer zentralen, kreisförmigen Einlassöffnung.The EP 0 410 271 B1 describes a radial fan for conveying a gaseous medium in a device with high flow resistance, which is in particular a burner in a gas boiler. Such burners have a relatively high flow resistance, which is of the order of 200 Pascal or more. The medium to be conveyed may be air or a combustible gas-air mixture. The blower or its blower wheel must therefore be designed for a steep pressure-volume flow characteristic. This means that pressure changes should be accompanied by only small changes in the volume flow. The known fan has for this purpose an impeller whose diameter is more than ten times its flow outlet width. It is a closed, both sides capped wheel with a substantially flat and a central hub having lower part (first cover plate), a plurality of backwardly curved, each having the shape of a circular section blades and a circular, flat plate-shaped lid (second cover plate ) with a central, circular inlet opening.

Auch die Dokumente DE 41 41 359 A1 , CH 301 116 und DE 102 04 037 A1 beschreiben jeweils ähnliche, ebenfalls geschlossene Gebläseräder, wobei gemäß den beiden ersten Dokumenten verkürzte Zwischenschaufeln vorgesehen sind.Also the documents DE 41 41 359 A1 . CH 301 116 and DE 102 04 037 A1 describe in each case similar, also closed impellers, wherein according to the first two documents shortened intermediate blades are provided.

Solche geschlossenen, beidseitig gedeckelten Radialgebläseräder sind relativ schwierig und aufwendig in der Herstellung.Such closed, double capped radial impellers are relatively difficult and expensive to manufacture.

Durch die WO 02/45862 A2 ist ein weiteres Radialgebläse bekannt, welches aber ein Gebläserad mit im Vergleich zum Durchmesser derart großer axialer Länge und Strömungsaustrittsbreite aufweist, dass dieses Gebläse nicht oder weniger gut für die bevorzugte Anwendung als Gasbrenner-Gebläse geeignet ist. Dieses bekannte Gebläserad weist durchweg gleich lange Schaufeln auf und ist auf der Nabenseite axial offen ausgebildet.By the WO 02/45862 A2 Another radial fan is known, but which has an impeller with compared to the diameter of such a large axial length and flow outlet width that this fan is not or less well suited for the preferred application as a gas burner blower. This known impeller has consistently the same length blades and is formed axially open on the hub side.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Radialgebläserad zu schaffen, welches bei besonderer Eignung für ein Gas-Brennergebläse mit steiler Kennlinie auf einfache und wirtschaftliche Weise herstellbar ist.The present invention has for its object to provide a Radialgebläserad, which is particularly suitable for a gas burner fan with steep curve in a simple and economical manner to produce.

Erfindungsgemäß wird dies durch die Merkmalskombination des Anspruchs 1 erreicht. Bevorzugte Ausgestaltungsmerkmale sind Gegenstand der abhängigen Ansprüche.This is achieved by the feature combination of claim 1 according to the invention. Preferred features are the subject of the dependent claims.

Bei einer erfindungsgemäßen Ausführungsform ist eine ringförmige Deckscheibe vorgesehen, die eine Breite RD aufweist, die vom Rand der Ansaugöffnung gemessen kleiner ist als der AbstandRand- Ansaugöffnung bis Austrittsöffnung - Umfangsrand.In one embodiment of the invention, an annular cover plate is provided which has a width R D , which is measured from the edge of the suction port is smaller than the AbstandRand- suction to discharge opening - peripheral edge.

Dabei ist es von Vorteil, mit die Breite so zu bemessen, dass sie die von der Ansaugöffnung gemessen im Wesentlichen eine halbe Schaufellänge beträgt. Diese besondere Ausgestaltung gestattet ebenfalls eine Herstellung des Gebläserads als einstückiges Formteil, wobei als besonders günstig eine Ausführungsform angesehen wird, bei der die Tragscheibe ringförmig ausgebildet ist und eine Ringbreite aufweist, die im wesentlichen dem Maß Außenrand Deckscheibe bis Austrittsöffnung -Umfangsrand (2-3') beträgt.In this case, it is advantageous to dimension the width such that it is substantially half the blade length measured from the intake opening. This particular embodiment also allows a production of the impeller as a one-piece molded part, being considered as particularly favorable an embodiment in which the support disc is annular and has a ring width, which is substantially the dimension outer edge cover plate to exit opening-Umfangsrand (2-3 '. ) is.

Wenn diese Ringbreite im Wesentlichen eine halbe Schaufellänge beträgt, kann dem Luftstrom im Austrittsbereich noch eine Führung erteilt werden, so dass die Scherreibung zwischen der rückwärtigen Gehäusewand und der Strömung auf einen reduzierten Bereich beschränkt ist.If this ring width is substantially half a blade length, the air flow in the exit region still a guide can be issued, so that the Scherbreibung between the rear housing wall and the flow is limited to a reduced range.

Dabei kann es günstig sein, dass sich die beiden Scheibenringe, nämlich der der Deckscheibe und derjenige der Tragscheibe, in der Projektion in Richtung Drehachse je nach Anforderung entweder überlappen, zwischen sich einen Spalt bilden oder sich an einander anschließend zu einer Kreisfläche ergänzen. Einen vorteilhaften Strömungsverlauf kann man dadurch erreichen, dass der Nabenkörper eine Höhe aufweist, die gemessen von der Ebene der rückwärtigen Tragscheibe im wesentlichen der halben Radtiefe entspricht. Günstigerweise ist an dem Nabenkörper zur Strömungsseite hin einen Konus ausgebildet, wobei die Deckscheibe und der Konus der Nabe im Querschnitt A-A im wesentlichen einen parallelen Verlauf aufweisen. Hierdurch wird ein günstiger Strömungsverlauf im Eingangsbereich des Rads erzielt.It may be favorable that the two disc rings, namely that of the cover disc and that of the support disc, either overlap in the projection in the direction of the axis of rotation as required, form a gap between them or subsequently complement each other to form a circular area. An advantageous flow course can be achieved in that the hub body has a height that corresponds to measured from the plane of the rear support plate substantially half the wheel depth. Conveniently, a cone is formed on the hub body to the flow side, wherein the cover plate and the cone of the hub in cross-section A-A have a substantially parallel course. As a result, a favorable flow profile is achieved in the input region of the wheel.

Bei einer vorteilhaften Ausgestaltung kann vorgesehen sein, dass am Außenumfang des Konus ein Bereich ausgebildet ist, dessen Strömungsoberfläche zur Rotationsebene im Wesentlichen parallel verläuft. Durch diese Ausbildung erhält die Strömung vor dem Verlassen des Konusbereichs noch eine Änderung im Richtungsgradienten, der ein steiles Auftreffen der Strömung im offenen Bereich des Rads hin reduziert.In an advantageous embodiment it can be provided that on the outer circumference of the cone, a region is formed whose flow surface is substantially parallel to the plane of rotation. By virtue of this design, the flow still receives a change in the directional gradient before leaving the cone region, which reduces a steep impingement of the flow in the open region of the wheel.

Dieser Effekt kann vorteilhafterweise noch dadurch gesteigert werden, dass die Strömungsoberfläche des Außenumfangsbereichs in einer Ebene angeordnet ist, die bezüglich des Strömungskanals weiter innen liegt als die den Strömungskanal begrenzende Fläche der äußeren Tragscheibe, d. h., es kann die Tragscheibe dünner ausgebildet werden als die Dicke des Außenumfangsbereichs des Konus.This effect can be advantageously further increased by the fact that the flow surface of the outer peripheral portion is arranged in a plane which is located with respect to the flow channel inwardly than the surface of the outer support disc defining the flow channel, d. That is, the support disk can be made thinner than the thickness of the outer peripheral portion of the cone.

Eine vorteilhafte Ausgestaltung kann so gestaltet sein, dass die Schaufeln im Ansaugbereich axial breiter sind als im Abströmbereich.An advantageous embodiment can be designed so that the blades are axially wider in the intake area than in the outflow area.

Günstig kann es auch sein, dass zwischen den Schaufeln im Wesentlichen im Bereich der Breite der Tragscheibe jeweils mindestens eine Zwischenschaufel angeordnet ist.It may also be favorable that in each case at least one intermediate blade is arranged between the blades essentially in the region of the width of the carrier disk.

Besonders günstig ist es, dass jeweils zwei Zwischenschaufeln paarweise angeordnet sind. Hierbei ist es besonders günstig, wenn die Zwischenschaufeln eine radiale Erstreckung aufweisen, die im Wesentlichen dem Abstand zwischen dem Außenumfang der Deckscheibe und dem Außenumfang der rückseitigen Tragscheibe entspricht.It is particularly favorable that in each case two intermediate blades are arranged in pairs. In this case, it is particularly favorable if the intermediate blades have a radial extension which essentially corresponds to the distance between the outer circumference of the cover disk and the outer circumference of the rear support disk.

Von besonderem Vorteil ist es, dass die Zwischenschaufeln ausschließlich an der rückseitigen Tragscheibe gehalten sind. Diese Ausführung erleichtert in besonders hohem Maße die Ausbildung des Radialgebläserads als ein einstückiges Gießteil.It is particularly advantageous that the intermediate blades are held exclusively on the rear support plate. This embodiment particularly facilitates the formation of the radial impeller as a one-piece cast part.

Zusammenfassend führt die erfindungsgemäße Merkmalskombination des Anspruchs 1 zu folgenden wesentlichen Vorteilen des Radialgebläserads:

  • insbesondere im Zusammenwirken mit einem geeignet angepassten Gebläsegehäuse geeignet für die Erzeugung eines hohen Drucks sowie zur Erzeugung einer steilen Kennlinie, bei der eine Änderung des Gegendrucks in der Anlage keine bzw. nur eine geringfügige Änderung des Volumenstromes bewirkt.
  • kurze axiale Baulänge
  • einteilige Fertigung im Kunststoff-Spritzverfahren mit einfacher Entformbarkeit und in einem einfachen und wirtschaftlichen Formwerkzeug
  • dadurch preisgünstig herstellbar.
In summary, the combination of features of claim 1 according to the invention leads to the following essential advantages of the radial impeller:
  • in particular in cooperation with a suitably adapted blower housing suitable for generating a high pressure and for generating a steep curve, in which a change in the backpressure in the system causes no or only a slight change in the flow rate.
  • short axial length
  • one-piece production in the plastic injection molding process with simple demolding and in a simple and economical mold
  • thereby inexpensive to produce.

Anhand von bevorzugten, in der Zeichnung veranschaulichten Ausführungsbeispielen soll die Erfindung genauer erläutert werden. Dabei zeigen:

Fig. 1
eine Perspektivansicht einer nicht-erfindungsgemäßen ersten Ausführungsform eines Radialgebläses auf die Seite der Deckscheibe,
Fig. 2
eine Perspektivansicht des Gebläserads gemäß Fig. 1 auf die andere, offene Seite der Schaufeln,
Fig. 3
eine Draufsicht auf die Seite der Deckscheibe,
Fig. 4
einen Querschnitt in der Ebene A-A gemäß Fig. 3,
Fig. 5
eine zweite Ausführungsform eines nicht-erfindungsgemäßen Radialgebläserads im Axialschnitt ähnlich Fig. 4,
Fig. 6
eine Darstellung analog zu Fig. 5 in einer nicht zur Erfindung gehörigen Weiterbildung,
Fig. 7
eine Draufsicht auf eine erfindungsgemäße Ausführungsform mit verkleinerter Deck- und Trägerscheibe und
Fig. 8
eine Ansicht eines Schnitts entlang der Linie A_A in Fig. 7
With reference to preferred embodiments illustrated in the drawings, the invention will be explained in more detail. Showing:
Fig. 1
a perspective view of a non-inventive first embodiment of a radial fan on the side of the cover plate,
Fig. 2
a perspective view of the impeller according to Fig. 1 on the other, open side of the blades,
Fig. 3
a plan view of the side of the cover plate,
Fig. 4
a cross section in the plane AA according to Fig. 3 .
Fig. 5
a second embodiment of a non-inventive radial impeller in axial section similar Fig. 4 .
Fig. 6
a representation analogous to Fig. 5 in a development not belonging to the invention,
Fig. 7
a plan view of an embodiment of the invention with reduced Cover and carrier disc and
Fig. 8
a view of a section along the line A_A in Fig. 7

In den verschiedenen Figuren der Zeichnung sind gleiche Teile stets mit den gleichen Bezugszeichen versehen.In the various figures of the drawing, like parts are always provided with the same reference numerals.

Ein Radialgebläserad 1 besteht aus einer Vielzahl von über den Umfang verteilt angeordneten Radial-Schaufeln 2, die in radialer Richtung gesehen von einem inneren Einlass bereich 4 zu einem äußeren Austrittsbereich 6 verlaufen. Gemäß Fig. 1 und 3 weisen die Schaufeln 2 radial innere Endkanten 8 auf, die auf einer gedachten, den Einlassbereich 4 umschließenden, etwa zylindrischen, insbesondere aber konischen und sich in der axialen Einströmrichtung (vgl. den Pfeil E in Fig. 1 und Fig. 4 bis 6) gesehen in den Einlassbereich 4 hinein verjüngenden Fläche liegen. Die Schaufeln 2 weisen ferner äußere Endkanten 10 auf. Jeweils zwischen den Schaufeln 2 sind radiale Startsmungskanäle 12 mit im Wesentlichen radialer Ausströmrichtung A gebildet.A radial impeller 1 consists of a plurality of distributed over the circumference arranged radial blades 2, seen in the radial direction of an inner inlet region 4 to an outer outlet region 6 extend. According to Fig. 1 and 3 The blades 2 have radially inner end edges 8, which are located on an imaginary, approximately cylindrical, but especially conical surrounding the inlet region 4 and in the axial inflow direction (see the arrow E in FIG Fig. 1 and 4 to 6 ) seen in the inlet region 4 in the tapered surface lie. The blades 2 also have outer end edges 10. In each case between the blades 2 radial Startsmungskanäle 12 are formed with a substantially radial outflow direction A.

Weiterhin verlaufen die Schaufeln 2 axial, d.h. in Richtung einer Drehachse 14 gesehen, zwischen einer Einlass-Seite 16 und einer axial gegenüberliegenden Nabenseite 18 (siehe hierzu die Schnittansichten in Fig. 4 bis 6).Furthermore, the blades 2 extend axially, ie viewed in the direction of a rotation axis 14, between an inlet side 16 and an axially opposite hub side 18 (see the sectional views in FIG 4 to 6 ).

Die Schaufeln 2 sind weiterhin nur auf deren Einlass-Seite 16 über ihre radiale Erstreckung hinweg bis zum Austrittsbereich 6 mit einer Deckscheibe 20 verbunden, die eine zentrische, in den Einlassbereich 4 mündende Einströmöffnung 22 aufweist. Auf der gegenüberliegenden Nabenseite 18 sind die Schaufeln jedoch nur mit ihren radial inneren Endbereichen mit einer zentrischen Nabe 24 verbunden, so dass die Strömungkanäle 12 auf dieser Seite in axialer Richtung offen ausgebildet sind. Die Schaufeln 2 weisen somit auf dieser Seite freie Seitenkanten 26 auf.The blades 2 are furthermore connected only on their inlet side 16 over their radial extent to the outlet region 6 with a cover disk 20 which has a central inlet opening 22 opening into the inlet region 4. On the opposite hub side 18, however, the blades are connected only with their radially inner end regions with a central hub 24, so that the flow channels 12 are formed open on this side in the axial direction. The blades 2 thus have free side edges 26 on this side.

Wie sich weiterhin aus Fig. 4 bis 6 ergibt, definieren die Schaufeln 2 und die Deckscheibe 20 einen äußeren Gebläserad-Durchmesser D, der mindestens das Zehnfache einer im Austrittsbereich 6 vorhandenen, axial gemessenen Strömungsaustrittsbreite B der Schaufeln beträgt. Dabei ist vorzugsweise die axial gemessene innere Strömungseintrittsbreite C der Schaufeln 2 im Einlassbereich 4 größer als die äußere Strömungsaustrittsbreite im Austrittsbereich 6 (vgl. z.B. Fig. 4).How to continue 4 to 6 results, define the blades 2 and the cover plate 20 has an outer impeller diameter D, which is at least ten times an existing in the exit region 6, axially measured flow outlet width B of the blades. In this case, the axially measured inner flow inlet width C of the blades 2 in the inlet region 4 is preferably greater than the outer flow outlet width in the outlet region 6 (cf., for example, FIG Fig. 4 ).

In weiterer nicht-erfindungsgemäßer Ausgestaltung sind mit der Deckscheibe 20 in jeweils zwischen benachbarten Schaufeln 2 angeordneten Bereichen radial kürzere Zwischenschaufeln 28 verbunden (siehe insbesondere Fig. 1 und 2). Diese Zwischenschaufeln 28 verlaufen vom äußeren Umfang der Deckscheibe 20 aus nur über einen Teil der radialen Erstreckung der Deckscheibe 20 und enden in einem radialen Abstand von der Nabe 24. Dies lässt sich am besten in Fig. 2 erkennen. In dem dargestellten Ausführungsbeispiel ist zwischen je zwei benachbarten Schaufeln 2 nur eine Zwischenschaufel 28 vorgesehen, es können aber auch je zwei oder mehr Zwischenschaufeln 28 vorgesehen sein, die dann mit gleicher oder unterschiedlicher radialer Länge ausgeführt sein können.In a further non-inventive embodiment are with the cover plate 20 in each radially disposed between adjacent blades 2 areas intermediate blades 28 are connected (see in particular Fig. 1 and 2 ). These intermediate blades 28 extend from the outer circumference of the cover plate 20 only over part of the radial extent of the cover plate 20 and terminate at a radial distance from the hub 24. This can best be seen in Fig. 2 detect. In the illustrated embodiment, between each two adjacent blades 2 only one intermediate blade 28 is provided, but it can also be provided each two or more intermediate blades 28, which can then be designed with the same or different radial length.

Durch die beschriebene Ausgestaltung kann das Radialgebläserad 1 vorteilhafterweise als einstückiges Formteil aus Kunststoff hergestellt werden, und zwar vorzugsweise aus einem Kunststoff mit derart antistatischen Eigenschaften, dass im Betrieb statische Aufladungen vermieden bzw, über ein nicht dargestelltes Gehäuse abgeleitet werden. Dies trägt zu einer hohen Anwendungssicherheit speziell im Hinblick auf die bevorzugte Anwendung zum Fördern von brennbaren Gas-Luftgemischen bei, indem Entzündungen durch Funkenbildung vermieden werden.Due to the described embodiment, the radial impeller 1 can be advantageously prepared as a one-piece molding made of plastic, preferably made of a plastic having such antistatic properties that during operation static charges avoided or derived via a not shown housing. This contributes to a high degree of application safety, especially with regard to the preferred application for conveying combustible gas-air mixtures, by avoiding ignition by sparking.

Wie sich aus Fig. 2 ergibt, ist bei diesem Ausführungsbeispiel vorgesehen, dass die Schaufeln 2 und die Zwischenschaufeln 28 in radialer Richtung bezogen auf die Drehrichtung 30 rückwärts gekrümmt ausgebildet sind. Hierbei sind die Schaufeln derart angeordnet, dass ihr Eintrittswinkel etwa zwischen 30° und 45° und ihr Austrittswinkel etwa zwischen 45° und 90° liegt. Zur Erläuterung dieser Winkel wird auf die EP 0 410 271 Bezug genommen. Alternativ ist aber auch eine Ausführung mit vorwärts gekrümmten oder am Austrittsbereich 6 radial endenden Schaufeln 2 und Zwischenschaufeln 28 möglich.As it turned out Fig. 2 results, it is provided in this embodiment that the blades 2 and the intermediate blades 28 are formed in the radial direction with respect to the direction of rotation 30 is curved backward. In this case, the blades are arranged such that their entry angle is approximately between 30 ° and 45 ° and their exit angle is approximately between 45 ° and 90 °. To explain this angle is on the EP 0 410 271 Referenced. Alternatively, however, an embodiment with forward curved or at the exit region 6 radially ending blades 2 and intermediate blades 28 is possible.

Die Nabe 24 besteht aus einem äußeren Scheibenabschnitt 32 und einem zentrischen, mit einer nicht dargestellten Welle zu verbindenden Lagerabschnitt 34 insbesondere in Form eines kurzen Rohransatzes. Dabei ist der Scheibenabschnitt 32 an seinem radial äußeren Umfang mit den inneren, dem Einlassbereich 4 zugekehrten Endbereichen der Schaufeln verbunden. Bei der ersten Ausführungsform gemäß Fig. 1 bis 4 ist vorteilhafterweise vorgesehen, dass der Scheibenabschnitt 32 der Nabe 24 ausgehend von seinem äußeren, mit den Schaufeln 2 verbundenen Umfangsbereich derart in den Einlassbereich 4 und in Richtung der Einströmöffnung 22 der Deckscheibe 20 vorspringend zum Beispiel konvex oder schalenartig geformt ist, dass die Nabe 24 - siehe hierzu insbesondere Fig. 4 - auf ihrer von der Einströmöffnung 22 wegweisenden Seite einen Aufnahmeraum 36 für bestimmte (nicht dargestellte) Gebläse-Funktionselemente wie Lagerelemente, Motor- bzw. Rotorteile und/oder dergleichen bildet. Diese vorteilhafte Ausgestaltung führt zu einer kurzen axialen Baulänge des gesamten Gebläses.The hub 24 consists of an outer disk portion 32 and a central, to be connected to a shaft not shown bearing portion 34, in particular in the form of a short pipe socket. In this case, the disc portion 32 is connected at its radially outer periphery with the inner, the inlet portion 4 facing end portions of the blades. In the first embodiment according to Fig. 1 to 4 is advantageously provided that the disc portion 32 of the hub 24 is projecting from its outer peripheral region connected to the blades 2 such in the inlet region 4 and in the direction of the inflow opening 22 of the cover plate 20 projecting convexly or cup-shaped, for example, that the hub 24 -. please refer in particular Fig. 4 - Forming on their side facing away from the inflow opening 22 a receiving space 36 for certain (not shown) blower-functional elements such as bearing elements, motor or rotor parts and / or the like. This advantageous embodiment leads to a short axial length of the entire fan.

Wie sich noch aus Fig. 2 ergibt, sind (zumindest) die Zwischenschaufeln 28 mit der Deckscheibe 20 über jeweils eine im Schaufel-Fußbereich gebildete Übergangsverstärkung 38 verbunden. Dies gewährleistet trotz der verbindungsfreien, von der Nabe 24 beabstandeten Ausgestaltung eine hinreichende Stabilität der Zwischenschaufeln 28.How to get out Fig. 2 shows, (at least) the intermediate blades 28 are connected to the cover plate 20 via a respective transition reinforcement 38 formed in the blade root area. This ensures, despite the connection-free, spaced from the hub 24 embodiment, a sufficient stability of the intermediate blades 28th

In einer weiteren, in Fig. 6 veranschaulichten nicht erfindungsgemäßen Ausgestaltung sind die Schaufeln 2 und die Zwischenschaufeln 28 in ihrem radial äußeren und der Deckscheibe 20 axial gegenüberliegenden Bereich zur mechanischen Verstärkung über ein umlaufendes, einstückig angeformtes Ringelement 40 verbunden.In another, in Fig. 6 illustrated embodiment, the blades 2 and the intermediate blades 28 in its radially outer and the cover plate 20 axially opposite region for mechanical reinforcement via a circumferential, integrally molded ring member 40 are connected.

Schließlich sei noch erwähnt, dass die Deckscheibe 20 im Bereich der Einströmöffnung 22 einen in Strömungsrichtung düsenartig geformten Rand 42 aufweist.Finally, it should be mentioned that the cover disk 20 in the region of the inflow opening 22 has a nozzle-like edge 42 in the flow direction.

In den Fig. 7 und 8 ist eine erfindungsgemäße Ausführungsvariante zur Lösung der Aufgabe dargestellt. Zum Unterschied zu den Bezugszeichen der vorangegangenen Ausführungsbeispiele sind beim nunmehr beschriebenen Ausführungsbeispiel die Bezugszeichen mit einer Ziffer 2 und Bindestrich versehen.In the Fig. 7 and 8th an embodiment of the invention for solving the problem is shown. In contrast to the reference numerals of the preceding embodiments, the reference numerals are provided with a number 2 and hyphen in the embodiment described now.

Das in Fig. 7 dargestellte Radialgebläserad 2-1 weist eine ringförmige Deckscheibe 2-9 auf, die den Ansaugbereich 2-7 ringförmig umgibt. Üblicherweise ist an der Deckscheibe 2-9 eine kreisförmige Ansaugöffnung 2-10 ausgebildet, die von einer umlaufenden Öffnungslippe 2-10' umgeben ist. Das Radialgebläserad 2-1 weist des Weiteren einen Nabenkörper 2-2 sowie einen Umfangsrand 2-3 auf. Der Nabenkörper 2-2 weist auf seiner der Ansaugöffnung 2-10 zugewandten Seite einen Konus 2-2' auf. Das Gebläserad 2-1 ist mit sich vom Nabenkörper 2-2 bis zum Umfangsrand 2-3 im Wesentlichen radial erstreckenden Schaufeln 2-6 ausgestattet. Durch die Schaufeln wird ein Ansaugbereich 2-7 und ein Abströmbereich 2-8 definiert.This in Fig. 7 shown radial impeller 2-1 has an annular cover plate 2-9, which surrounds the suction 2-7 annular. Usually, a circular suction opening 2-10 is formed on the cover plate 2-9, which is surrounded by a circumferential opening lip 2-10 '. The radial impeller 2-1 further includes a hub body 2-2 and a peripheral edge 2-3. The hub body 2-2 has on its side facing the suction opening 2-10 a cone 2-2 'on. The impeller 2-1 is equipped with blades 2 - 6 substantially extending radially from the hub body 2 - 2 to the peripheral edge 2-3. The vanes define an intake region 2-7 and an outflow region 2-8.

Die ringförmige Deckscheibe 2-9 weist eine Breite RD auf, die vom Rand der Ansaugöffnung (2-10) gemessen die Hälfte des Abstands Rand-Austrittsöffnung -Umfangsrand 2-3 beträgt.The annular cover plate 2-9 has a width R D , which measured from the edge of the suction port (2-10) is half the distance edge-outlet opening circumference 2-3.

Die Breite RD entspricht somit im Wesentlichen der Hälfte der Schaufellänge gemessen entlang der oberen Randkante der Schaufel 2-6.The width R D thus corresponds substantially to half the blade length measured along the upper peripheral edge of the blade 2-6.

Der Fuß einer solchen Schaufel ist an seiner radial innenliegenden Spitze mit dem Nabenkörper einstückig verbunden. Die sich auf der Rückseite 2-5 erstreckende Tragscheibe 2-11 ist ringförmig ausgebildet und weist an ihrem Ring eine Breite RT auf, die, vom Rand der Ansaugöffnung 2-10 gemessen, im Wesentlichen die Hälfte der Bemessung Rand Austrittsöffnung 2-10- Umfangsrand 2-3 beträgt. Dies entspricht im Wesentlichen eine halbe Schaufellänge, gemessen entlang der rückseitigen Kante des Schaufelstrahls zwischen Umfangsrand 2-3 und Fußpunkt der Schaufel 2-6 an dem Konus 2-2' der Nabe 2-2.The foot of such a blade is integrally connected at its radially inner tip with the hub body. The support disk 2-11 extending on the rear side 2-5 is annular and has at its ring a width R T which, measured from the edge of the suction opening 2-10, is substantially half of the dimension of the edge outlet opening 2-10- Peripheral edge is 2-3. This substantially corresponds to half a blade length measured along the back edge of the blade jet between peripheral edge 2-3 and bottom of the blade 2-6 on the cone 2-2 'of the hub 2-2.

Bei einer derartigen Bemessung sind, wie in Fig. 7 zu erkennen, in der Projektion des Gebläserads auf die Ebene der Tragscheibe in Richtung der Drehachse der Außenumfang der Deckscheibe 2-9 und der Innenumfang der Tragscheibe 2-11 deckungsgleich. Alternative Ausführungsformen können jedoch vorsehen, dass sich beide Scheibenringe 2-9; 2-11 je nach Anforderung in der Projektion in Richtung Drehachse 2-12 überlappen oder zwischen sich einen Spalt bilden.In such a design, as in Fig. 7 to recognize, in the projection of the impeller on the plane of the support disk in the direction of the axis of rotation of the outer periphery of the cover plate 2-9 and the inner circumference of the support plate 2-11 congruent. However, alternative embodiments may provide that both disc rings 2-9; Depending on the requirements in the projection, overlap 2-11 in the direction of the axis of rotation 2-12 or form a gap between them.

Der Nabenkörper 2-2 weist eine Höhe auf, die, gemessen von der Ebene von der rückwärtigen Tragscheibe 2-11 im Wesentlichen der halben Radhöhe entspricht. Im dargestellten Ausführungsbeispiel entspricht die Höhe der Nabe der Hälfte der Höhe der in die Ansaugöffnung 2-10 hineinragenden Schaufeln.The hub body 2-2 has a height that, measured from the plane of the rear support plate 2-11 substantially equal to half the wheel height. In the illustrated embodiment, the height of the hub corresponds to half the height of the projecting into the suction port 2-10 blades.

Die Oberfläche FK des Konus 2-2' der Nabe 2-2 verläuft im Wesentlichen parallel zur inneren Fläche FD Deckscheibe 2-9. Im Bereich des Fußes des Konus, d.h. an seinem Außenumfang, ist ein Bereich 2-21 ausgebildet, dessen Oberfläche zur Rotationsebene des Gebläserads im Wesentlichen parallel verläuft. Die der Strömung zugewandte Oberfläche des Konus und der rotationsparallele Bereich sind dabei ausgerundet. Zwischen den sich vom Rand der Ansaugöffnung 2-10 bis zum Umfangsrand 2-3 des Gebläserads 2-1 erstreckenden Schaufeln 2-6 sind im wesentlichen im Bereich der Breite der rückseitigen Tragscheibe 2-11 Zwischenschaufeln 2-16 angeordnet. Die Anzahl der Zwischenschaufeln 2-16 kann je nach Einsatzgebiet variieren. Vorzugsweise sind bei dem dargestellten Ausführungsbeispiel zwei Zwischenschaufeln 2-16 paarweise zwischen zwei Schaufeln 2-6 angeordnet. Die radiale Erstreckung der Zwischenschaufeln 2-16 ist so bemessen, dass sie im wesentlichen dem Abstand 2-17 zwischen dem Außenumfang 2-18 der Deckscheibe 2-9 und dem Außenumfang 2-19 der rückseitigen Tragscheibe 2-11 entspricht. Bei dem dargestellten Ausführungsbeispiel sind die Zwischenschaufeln 2-16 ausschließlich an der rückseitigen Tragscheibe 2-11 gehalten, d. h., die vorderen Kanten der Zwischenschaufeln sind bei dieser Ausführungsform frei. Je nach oben beschriebener Anordnung der Deck- und der Tragscheibe können die Zwischenschaufeln jedoch auch an der Deckscheibe angeformt sein. Die Gestalt der Zwischenschaufeln entspricht in ihrem Verlauf im Wesentlichen der entsprechenden Gestaltung des Abschnitts der Schaufeln 2-6 an entsprechender Stelle.The surface F K of the cone 2-2 'of the hub 2-2 extends substantially parallel to the inner surface F D cover plate 2-9. In the region of the foot of the cone, ie on its outer circumference, a region 2-21 is formed, the surface of which runs essentially parallel to the plane of rotation of the impeller. The flow-facing surface of the cone and the rotation-parallel region are rounded. Between the blades 2-6 extending from the edge of the suction opening 2-10 to the peripheral edge 2-3 of the fan wheel 2-1, intermediate blades 2-16 are arranged substantially in the region of the width of the rear support disk 2-11. The number of blades 2-16 may vary depending on the application. Preferably In the illustrated embodiment, two intermediate blades 2-16 are arranged in pairs between two blades 2-6. The radial extent of the intermediate blades 2-16 is dimensioned so that it substantially corresponds to the distance 2-17 between the outer periphery 2-18 of the cover plate 2-9 and the outer periphery 2-19 of the rear support plate 2-11. In the illustrated embodiment, the intermediate blades 2-16 are held exclusively on the rear support plate 2-11, that is, the front edges of the intermediate blades are free in this embodiment. Depending on the above-described arrangement of the cover and the support disk but the intermediate blades can also be formed on the cover plate. The shape of the intermediate blades corresponds in its course substantially the corresponding design of the portion of the blades 2-6 at the appropriate location.

Die Ausführungsform kann vorteilhafterweise als einstückiges Formteil aus Kunststoff hergestellt werden.The embodiment can be advantageously manufactured as a one-piece molded part made of plastic.

Claims (13)

  1. Radial fan impeller (2-1) comprising
    a hub element (2-2) and a peripheral edge,
    a front side (2-4) and a rear side (2-5),
    blades (2-6) extending substantially radially from the hub element (2-2) to the peripheral edge,
    an intake region (2-7) and an outflow region (2-8),
    with an annular covering disc (2-9) on the front side in which an intake opening (2-10) is formed and with a rear-side support disc (2-11), characterised in that the annular covering disc (2-9) has a width RD which, measured from the edge of the intake opening (2-10), is smaller than the distance edge-intake opening (2-10) to discharge opening-circumferential edge (2-3').
  2. Radial fan impeller according to Claim 1, characterised in that the width RD is substantially half of a blade length.
  3. Radial fan impeller according to Claim 1, characterised in that the support disc (2-11) is annular in form and has an annular width RT which is substantially the measurement outer edge covering disc to discharge opening-circumferential edge (2-3').
  4. Radial fan impeller according to Claim 1, characterised in that both disc rings (2-9, 2-11) overlap in the projection in the direction of the rotation axis (2-12), form a gap between them or complement one another, adjoining to form a circular surface, depending upon the requirement.
  5. Radial fan impeller according to any of the preceding Claims 1 to 4, characterised in that the hub element (2-2) has a height which, measured from the plane of the rear support disc substantially corresponds to half of the impeller height.
  6. Radial fan impeller according to any of the preceding claims 1 to 5, characterised in that the hub element (2-2) towards the flow side has a cone (2-2'), and the covering disc (2-9) and the cone of the hub in the cross-section A-A have a substantially parallel course.
  7. Radial fan impeller according to Claim 6, characterised in that on the outer circumference of the cone (2-2') a region (2-21) is formed, the surface of which extends substantially parallel to the rotation plane.
  8. Radial fan impeller according to any of the preceding Claims 1 to 7, characterised in that at least one intermediary blade (16) is respectively disposed between the blades (6), substantially in the region of the width of the rear-side support disc (11).
  9. Radial fan impeller according to Claim 8 characterised in that two intermediary blades (16) are respectively disposed in pairs.
  10. Radial fan impeller according to Claim 8 or 9, characterised in that the intermediary blades (16) have a radial extension which substantially corresponds to the distance (17) between the outer circumference (18) of the covering disc (9) and the outer circumference (19) of the rear-side support disc (11).
  11. Radial fan impeller according to any of the preceding Claims 8 to 10, characterised in that the intermediary blades (2-16) are only held on the rear-side support disc (2-11).
  12. Radial fan impeller according to Claim 1 and those following, characterised by a design as a one-piece moulded part made of synthetic.
  13. Radial fan impeller according to Claim 12, characterised in that the moulded part is made of a synthetic with anti-static properties such that during operation, static charges are avoided or dissipated.
EP10157619.7A 2004-07-31 2005-07-29 Impeller for a radial fan Active EP2196679B1 (en)

Applications Claiming Priority (2)

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DE202004012015U DE202004012015U1 (en) 2004-07-31 2004-07-31 radial impeller
EP05768016A EP1774180B1 (en) 2004-07-31 2005-07-29 Radial fan wheel

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EP2196679A3 EP2196679A3 (en) 2013-12-18
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AT (1) ATE544953T1 (en)
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EP2196679A2 (en) 2010-06-16
EP2196679A3 (en) 2013-12-18
US20080292464A1 (en) 2008-11-27
DE202004012015U1 (en) 2005-12-22
ATE544953T1 (en) 2012-02-15
US7794206B2 (en) 2010-09-14
US8109731B2 (en) 2012-02-07
US20100098544A1 (en) 2010-04-22
EP1774180A2 (en) 2007-04-18
EP1774180B1 (en) 2012-02-08
WO2006013067A2 (en) 2006-02-09
WO2006013067A3 (en) 2006-12-28

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