EP1774180B1 - Radial fan wheel - Google Patents

Radial fan wheel Download PDF

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Publication number
EP1774180B1
EP1774180B1 EP05768016A EP05768016A EP1774180B1 EP 1774180 B1 EP1774180 B1 EP 1774180B1 EP 05768016 A EP05768016 A EP 05768016A EP 05768016 A EP05768016 A EP 05768016A EP 1774180 B1 EP1774180 B1 EP 1774180B1
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EP
European Patent Office
Prior art keywords
blades
radial
fan wheel
region
hub
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EP05768016A
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German (de)
French (fr)
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EP1774180A2 (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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Priority to EP10157619.7A priority Critical patent/EP2196679B1/en
Publication of EP1774180A2 publication Critical patent/EP1774180A2/en
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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
    • 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, as defined in the preamble of claim 1.
  • the EP 0 410 271 B1 describes such 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.
  • a burner in a gas boiler Such burners have a relatively high flow resistance, which is on the order of 200 Pascal and more.
  • the medium to be delivered 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.
  • the diameter as at least ten times the flow outlet width of the blades, the desired steep characteristic is achieved.
  • the blades have on their side facing away from the cover plate side free edges, which lie in an imaginary plane or any curved surface.
  • the radial impeller according to the invention is intended for use in a blower housing which has a wall adapted to the free blade side edges or to the imaginary surface shape defined by these, such that only a narrow axial gap is formed between this wall and the impeller blades ,
  • the invention provided in each case between two blades shortened intermediate blades have the advantage that on the one hand a relatively large number of blades or vanes can be provided, which is advantageous in terms of flow guidance in the flow channels formed between the blades with regard to air flow, flow separation and vortex formation.
  • the problem is avoided that with a correspondingly large number of long, to the inlet area - continuous blades of the intake or inflow would be partially blocked, which would have a negative effect on the delivery volume.
  • the radially inner inflow region is kept open in the region of the shorter intermediate vanes.
  • annular cover plate which has a width R D , which is measured from the edge of the suction port is smaller than the distance between the edge suction port to outlet port-peripheral edge.
  • width is such that it is measured from the intake substantially half a blade length.
  • This particular embodiment also allows a manufacture of the impeller as a one-piece molding, which is considered to be particularly favorable a shape in which the support disk is annular and has an annular width which is substantially the dimension outer edge of the cover plate to the outlet opening-Umfangsrand (2-3 ').
  • this ring width is substantially half a blade length, guidance can still be given to the airflow in the exit region, so that the shear friction between the rearward housing wall and the flow is restricted 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 complement each other then to 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 (2-9) 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 on the outer circumference of the cone whose flow surface is essentially parallel to the plane of rotation.
  • An advantageous embodiment can be designed so that the blades are axially wider in the intake area than in the outflow area.
  • a radial impeller 1 consists of a plurality of circumferentially distributed radial blades 2, which extend in the radial direction from an inner inlet region 4 to an outer outlet region 6.
  • Fig. 1 and 3 have the blades 2 radially inner end edges 8, which on an imaginary, the inlet portion 4 enclosing, about cylindrical, but in particular conical and in the axial Inflow direction (see the arrow E in 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 flow channels 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 centric inlet opening 22 opening into the inlet region 4.
  • a cover disk 20 which has a centric 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. Fig. 4 ).
  • radially shorter intermediate blades 28 are connected to the cover disk 20 in each area arranged between adjacent blades 2 (see in particular FIG 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 example shown is between two each 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 static charges are avoided during operation or derived via a housing, not shown. 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 backward curved.
  • 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 Endbsever 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 -. see in particular Fig.
  • 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 are connected in their radially outer and the cover plate 20 axially opposite region for mechanical reinforcement via a circumferential, integrally molded ring member 40.
  • the cover disk 20 in the region of the inflow opening 22 has a nozzle-like edge 42 in the flow direction.
  • Fig. 7 and 8th is another example not within the scope of this invention. Unlike the reference numerals of the preceding embodiments are described now. Embodiment provided the reference numerals with a numeral 2 and hyphen.
  • 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 with itself from the hub body 2-2 to the peripheral edge 2-3 substantially radially extending blades 2-6 equipped.
  • 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 to substantially half of 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 plate 2-11 extending on the back 2-5 is annular and has at its ring a width RT, which, measured from the edge of the suction port 2-10, substantially half of the design edge outlet opening 2-10 - peripheral edge 2-3. This corresponds essentially to half the length of the blade, measured along the back edge of the blade jet between the peripheral edge 2-3 and the base of the blade 2-6 on the cone 2-2 'of the hub 2-2.
  • the hub body 2-2 has a height which, measured from the plane of the rear support plate 2-11 substantially equal to half the wheel height. In the example shown, the height of the hub corresponds to half the height of the blades projecting into the intake opening 2-10.
  • 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, whose surface is substantially parallel to the plane of rotation of the impeller.
  • the surface facing the flow, 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. Preferably, in the illustrated example, 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 Z-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 leading edge of the intermediate blades are free in this example.
  • the intermediate blades can also be formed on the cover plate.
  • the shape of the intermediate blades essentially corresponds to the corresponding design of the section of the blades 2-6 at the appropriate location.
  • the preceding example can advantageously also be produced 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, wie im Oberbegriff vom Anspruch 1 definiert.The present invention relates to a radial impeller, in particular for use in gas blowers with a steep fan characteristic, as defined in the preamble of claim 1.

Die EP 0 410 271 B1 beschreibt ein solches 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 such 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 on the order of 200 Pascal and more. The medium to be delivered 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 about 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 abhangigen Ansprüche.This is achieved by the feature combination of claim 1 according to the invention. Preferred features are subject of the dependent claims.

Durch die Auslegung des Durchmessers als mindestens das zehnfache der Strömungsaustrittsbreite der Schaufeln wird die angestrebte steile Kennlinie erreicht. Erfindungsgemäß weisen dabei aber die Schaufeln auf ihrer von der Deckscheibe wegweisenden Seite freie Seitenkanten auf, die in einer gedachten ebenen oder beliebig gewölbten Fläche liegen. Durch diese erfindungsgemäß auf dieser Seite offene Ausbildung des Gebläserades kann dieses sehr schnell und wirtschaftlich als einstückiges Formteil im Spritzverfahren aus Kunststoff hergestellt werden, indem ein relativ einfaches Spritzwerkzeug ohne oder mit nur wenigen Schiebern verwendet werden kann, weil durch den.Aufbau des Rades Hinterschneidungen in Entformrichtung vermieden werden können, so dass eine einfach axiale Entformung des Formteiles möglich istBy designing the diameter as at least ten times the flow outlet width of the blades, the desired steep characteristic is achieved. According to the invention, however, the blades have on their side facing away from the cover plate side free edges, which lie in an imaginary plane or any curved surface. By this invention On this page open design of the fan wheel this can be made very quickly and economically as a one-piece molding in the injection molding of plastic by a relatively simple injection tool can be used without or with only a few sliders, because by den.Aufbau the wheel undercuts are avoided in Entformrichtung can, so that a simple axial demolding of the molded part is possible

Das erfindungsgemäße Radialgebläserad ist zum Einsatz in einem Gebläsegehäuse vorgesehen, welches eine an die freien Schaufel-Seitenkanten bzw. an die von diesen definierte, gedachte Flächenform derart angepasste Wandung aufweist, dass zwischen dieser Wandung und den Gebläserad-Schaufeln nur ein schmaler axialer Spalt gebildet ist.The radial impeller according to the invention is intended for use in a blower housing which has a wall adapted to the free blade side edges or to the imaginary surface shape defined by these, such that only a narrow axial gap is formed between this wall and the impeller blades ,

Die erfindungsgemäß jeweils zwischen zwei Schaufeln vorgesehenen verkürzten Zwischenschaufeln haben den Vorteil, dass einerseits insgesamt eine relativ große Anzahl von Schaufeln bzw. Zwischenschaufeln vorgesehen sein kann, was bezüglich der Strömungsführung in den zwischen den Schaufeln gebildeten Strömungskanälen hinsichtlich Luftführung, Strömungsablösungen und Wirbelbildung vorteilhaft ist. Andererseits wird aber das Problem vermieden, dass bei einer entsprechend großen Anzahl von langen, bis zum Einlassbereich - durchgehenden Schaufeln der Ansaug- bzw. Einströmbereich teilweise versperrt wäre, was sich negativ auf das Fördervolumen auswirken würde. Erfindungsgemäß wird demgegenüber im Bereich der kürzeren Zwischenschaufeln der radial innere Einströmbereich offengehalten.The invention provided in each case between two blades shortened intermediate blades have the advantage that on the one hand a relatively large number of blades or vanes can be provided, which is advantageous in terms of flow guidance in the flow channels formed between the blades with regard to air flow, flow separation and vortex formation. On the other hand, however, the problem is avoided that with a correspondingly large number of long, to the inlet area - continuous blades of the intake or inflow would be partially blocked, which would have a negative effect on the delivery volume. In contrast, according to the invention, the radially inner inflow region is kept open in the region of the shorter intermediate vanes.

Bei einer nicht hier mit geschützten Form ist eine ringförmige Deckscheibe vorgesehen, die eine Breite RD aufweist, die vom Rand der Ansaugöffnung gemessen kleiner ist als der Abstand Rand- Ansaugöffnung bis Austrittsöffnung -Umfangsrand.In a not protected here form 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 distance between the edge suction port to outlet port-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 Form 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.It is advantageous with the width to be such that it is measured from the intake substantially half a blade length. This particular embodiment also allows a manufacture of the impeller as a one-piece molding, which is considered to be particularly favorable a shape in which the support disk is annular and has an annular width which is substantially the dimension outer edge of the cover plate to the outlet opening-Umfangsrand (2-3 ').

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 istIf this ring width is substantially half a blade length, guidance can still be given to the airflow in the exit region, so that the shear friction between the rearward housing wall and the flow is restricted 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 ein Konus ausgebildet, wobei die Deckscheibe (2-9) 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 complement each other then to 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 (2-9) 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.

Es 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.It can be provided; a region is formed on the outer circumference of the cone whose flow surface is essentially 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 flow channel limiting surface of the outer support disc, ie, it can Support disk are formed 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 SchaufelnIt may also be favorable that between the blades

jeweils zwei Zwischenschaufeln paarweise angeordnet sind.two intermediate blades are arranged in pairs.

Zusammenfassend führt die erfindungsgemäße Merkmalskombination 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 feature combination 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 folgender Zeichnungen soll sowohl der allgemeine Aufbau eines Radialgebläses, als auch die Erfindung genauer erläutert werden. Dabei zeigen:

  • Fig. 1 eine Perspektivansicht eines nicht in den Schutzumfang dieser Erfindung gehörenden 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 Form eines nicht in den Schutzumfang dieses Erfindung gehörenden Radiaigebläserads im Axialschnitt ähnlich Fig. 4,
  • Fig. 6 eine Darstellung analog zu Fig. 5 eines Radialgebläses nach der Erfindung,
  • Fig. 7 eine Draufsicht auf eines weiteren Radialgebläses mit verkleinerter Deck- und Trägerscheibe und
  • Fig. 8 eine Ansicht eines Schnitts entlang der Linie A_A in Fig. 7
Reference to the following drawings, both the general structure of a radial fan, and the invention will be explained in more detail. Showing:
  • Fig. 1 a perspective view of a not belonging to the scope of this invention 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 form of a Radiaigebläser not belonging to the scope of this invention in axial section similar Fig. 4 .
  • Fig. 6 a representation analogous to Fig. 5 a radial fan according to the invention,
  • Fig. 7 a plan view of another radial fan with reduced cover and carrier disk 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 Einlassbereich 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 Strömungskanäle 12 mit im wesentlichen radialer Ausströmrichtung A gebildet.A radial impeller 1 consists of a plurality of circumferentially distributed radial blades 2, which extend in the radial direction from an inner inlet region 4 to an outer outlet region 6. According to Fig. 1 and 3 have the blades 2 radially inner end edges 8, which on an imaginary, the inlet portion 4 enclosing, about cylindrical, but in particular conical and in the axial Inflow direction (see the arrow E in 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 flow channels 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 Strömungskanäle 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 centric 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. Fig. 4 ).

In weiterer 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 Beispiel 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 embodiment, radially shorter intermediate blades 28 are connected to the cover disk 20 in each area arranged between adjacent blades 2 (see in particular FIG 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 example shown is between two each 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 static charges are avoided during operation or derived via a housing, not shown. 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 Beispiel 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 example that the blades 2 and the intermediate blades 28 are formed in the radial direction with respect to the direction of rotation 30 backward curved. 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 Endbsreichen der Schaufeln verbunden. Bei dem ersten Beispiel 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 Endbsreichen the blades. In the first example 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 -. see in particular Fig. 4 - On its side facing away from the inflow opening 22 side forms a receiving space 36 for certain (not shown) fan-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 der in, in Fig. 6 veranschaulichten Ausgestaltung der Erfindung 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 the in, in Fig. 6 illustrated embodiment of the invention, the blades 2 and the intermediate blades 28 are connected in their radially outer and the cover plate 20 axially opposite region for mechanical reinforcement via a circumferential, integrally molded ring member 40.

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 ein weiteres nicht in dem Schutzumfang dieses Erfindung gehörendes Beispiel. 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 is another example not within the scope of this invention. Unlike the reference numerals of the preceding embodiments are described now. Embodiment provided the reference numerals with a numeral 2 and hyphen.

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 with itself from the hub body 2-2 to the peripheral edge 2-3 substantially radially extending blades 2-6 equipped. 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.
Die Breite RD entspricht somit im wesentlichen der Hälfte der Schaufellänge gemessen entlang der oberen Randkante der Schaufel 2-6.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 to substantially half of 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 plate 2-11 extending on the back 2-5 is annular and has at its ring a width RT, which, measured from the edge of the suction port 2-10, substantially half of the design edge outlet opening 2-10 - peripheral edge 2-3. This corresponds essentially to half the length of the blade, measured along the back edge of the blade jet between the peripheral edge 2-3 and the base 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 Formen 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 forms 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 Beispiel 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 which, measured from the plane of the rear support plate 2-11 substantially equal to half the wheel height. In the example shown, the height of the hub corresponds to half the height of the blades projecting into the intake opening 2-10.

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 2-14 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 das 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 ersteckenden 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 Beispiel 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 Z-17 zwischen dem Außenumfang 2-18 der Deckscheibe 2-9 und dem Außenumfang 2-19 der rückseitigen Tragscheibe 2-11 entspricht. Bei dem dargestellten Beispiel sind die Zwischenschaufeln 2-16 ausschließlich an der rückseitigen Tragscheibe 2-11 gehalten, d. h., die vordere Kante der Zwischenschaufeln sind bei diesem Beispiel frei. Je nach oben beschriebener Anordnung der Deck- und der Tragscheibe können die Zwischenschaufeln jedoch auch an der Deckscheibe angeformt sein. Die Gestalt der Zwlschenschaufeln 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 area of the foot 2-14 of the Cone, ie on its outer circumference, a region 2-21 is formed, whose surface is substantially parallel to the plane of rotation of the impeller. The surface facing the flow, 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 example, 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 Z-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 example, the intermediate blades 2-16 are held exclusively on the rear support plate 2-11, that is, the leading edge of the intermediate blades are free in this example. 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. In its course, the shape of the intermediate blades essentially corresponds to the corresponding design of the section of the blades 2-6 at the appropriate location.

Wie bereits das erste Beispiel, so kann auch das vorangehende Beispiel vorteilhafterweise als einstückiges Formteil aus Kunststoff hergestellt werdenAs in the first example, the preceding example can advantageously also be produced as a one-piece molded part made of plastic

Claims (10)

  1. Radial fan wheel (1), In particular for using In gas fans having a steep fan characteristic curve, having the following features:
    having a plurality of blades (2) distributed over the periphery;
    viewed in the radial direction, the blades (2) extend from an inner inlet region (4) to an outer discharge region (6);
    the blades (2) extend axially, i.e. viewed In the direction of a rotation axis (14), between an inlet side (16) and an axially opposite hub side (18);
    on the inlet side (16) the blades (2) are connected over their radial extension as far as the discharge region (6) to a covering disc (20) which has a central inflow opening (22) out Into the Inlet region (4);
    the blades (2) and the covering disc (20) define an outer fan wheel diameter (D) which is at least ten times an axially measured flow discharge width (B) of the blades (2) provided In the discharge region (6),
    characterised in that on the hub side (18) the blades (2) are only connected by their radial inner end regions to a central hub (24),
    radially shorter intermediary blades (28) are provided, which are connected to the covering disc (20) In regions respectively disposed between adjacent blades (2), and which extend from the outer circumference of the covering disc (20) over just one portion of the radial extension of the covering disc (20), and end a radial distance from the hub (24), and
    in their radially outer region which lies axially opposite the covering disc (20), the blades (2) and the intermediary blades (28) are connected by means of a circumferential annular element (40) In order to provide reinforcement.
  2. Radial fan wheel according to claim 1,
    characterised by a formation as a one-piece moulded part made of plastics material.
  3. Radial fan wheel according to claim 1,
    characterised in that the moulded part is made of a plastics material having anti-static properties such that during operation static charges are avoided or dissipated.
  4. Radial fan wheel according to any one of claims 1 to 2,
    characterised In that the blades (2) and/or the intermediary blades (28), in the radial direction based on the direction of rotation (30), extend bent backwards or bent forwards.
  5. Radial fan wheel according to any one of claims 1 to 3,
    characterised in that the blades (2) and/or the intermediary blades (28) extend ending radially at the discharge region (6).
  6. Radial fan wheel according to any one of claims 1 to 4,
    characterised in that the hub (24) consists of a disc portion (32) connected at Its radially outer circumference to the inner end regions, facing the Inlet region (4), of the blades (2) and a central mounting portion (34) to be connected to a shaft.
  7. Radial fan wheel according to claim 6,
    characterised In that the disc portion (32) of the hub (24), starting from Its outer peripheral region connected to the blades (2), Is formed into the inlet region (4) and towards the inflow opening (22) of the covering disc (20) such that the hub (24), on Its side facing away from the inflow opening (22) forms an accommodation space (36) for certain fan function elements such as bearing elements, motor and rotor parts and/or the like.
  8. Radial fan wheel according to any one of claims 1 to 6,
    characterised In that at least the intermediary blades (28) are connected to the covering disc (20) by means of a respective transition reinforcement (38).
  9. Radial fan wheel according to any one of claims 1 to 8,
    characterised In that In the region of the inflow opening (22) the covering disc (20) has an edge (42) In the form of a nozzle In the direction of flow.
  10. Radial fan wheel according to any one of claims 1 to 8,
    characterised In that an inner flow inlet width (C) of the blades (2) is greater than the outer flow discharge width (B).
EP05768016A 2004-07-31 2005-07-29 Radial fan wheel Active EP1774180B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10157619.7A EP2196679B1 (en) 2004-07-31 2005-07-29 Impeller for a radial fan

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004012015U DE202004012015U1 (en) 2004-07-31 2004-07-31 radial impeller
PCT/EP2005/008250 WO2006013067A2 (en) 2004-07-31 2005-07-29 Radial fan wheel

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EP10157619.7A Division EP2196679B1 (en) 2004-07-31 2005-07-29 Impeller for a radial fan
EP10157619.7 Division-Into 2010-03-24

Publications (2)

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EP1774180A2 EP1774180A2 (en) 2007-04-18
EP1774180B1 true EP1774180B1 (en) 2012-02-08

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EP05768016A Active EP1774180B1 (en) 2004-07-31 2005-07-29 Radial fan wheel
EP10157619.7A Active EP2196679B1 (en) 2004-07-31 2005-07-29 Impeller for a radial fan

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US (2) US7794206B2 (en)
EP (2) EP1774180B1 (en)
AT (1) ATE544953T1 (en)
DE (1) DE202004012015U1 (en)
WO (1) WO2006013067A2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022003842A1 (en) 2021-10-19 2023-04-20 Truma Gerätetechnik GmbH & Co. KG impeller

Families Citing this family (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4935048B2 (en) * 2005-10-27 2012-05-23 日本電産株式会社 Centrifugal fan
WO2008052292A1 (en) * 2006-11-03 2008-05-08 Resmed Ltd Single or multiple stage blower and nested volute(s) and/or impeller(s) therefor
ITPN20060004U1 (en) * 2006-02-15 2007-08-16 Electrolux Home Prod Corp DOMESTIC TOWEL DRYER WITH DOUBLE FAN.
TWI306921B (en) * 2006-07-21 2009-03-01 Delta Electronics Inc Fan and impeller thereof
EP2074361A4 (en) * 2006-10-19 2013-03-06 Lg Electronics Inc Cool air supplying apparatus used in refrigerator and refrigerator having the same
ATE466195T1 (en) * 2007-11-12 2010-05-15 Elica Spa WHEEL FOR A CENTRAL BLOWER AND CENTRAL BLOWER
US8007241B2 (en) 2007-11-27 2011-08-30 Nidec Motor Corporation Bi-directional cooling fan
JP5267343B2 (en) * 2008-06-14 2013-08-21 日本電産株式会社 Impeller and centrifugal fan
DE102009028130A1 (en) * 2009-07-30 2011-02-03 Robert Bosch Gmbh Guide geometry for semi-axial fan wheels
DE102009056837A1 (en) * 2009-12-10 2011-06-22 ebm-papst Landshut GmbH, 84030 mixing fan
CN103282672A (en) * 2011-01-05 2013-09-04 博格华纳公司 Impeller design for fluid pump assembly and method of making
JP5832804B2 (en) 2011-07-25 2015-12-16 ミネベア株式会社 Centrifugal fan
CN102418714B (en) * 2011-12-20 2014-06-11 林钧浩 Centrifugal fan capable of diversion, pressure increase and energy saving
RU2516739C1 (en) * 2012-11-12 2014-05-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) Blade of axial flow fan
US20140157613A1 (en) * 2012-12-12 2014-06-12 General Electric Company Fan assembly for an appliance
KR101577875B1 (en) * 2013-12-30 2015-12-28 동부대우전자 주식회사 Centrifugal fan for refrigerator
ES2773899T3 (en) 2014-03-17 2020-07-15 Elica Spa A rotor for a radial fan and a radial fan
CN204628024U (en) * 2014-04-18 2015-09-09 许铭海 Fan with cooling device
DE102014006756A1 (en) 2014-05-05 2015-11-05 Ziehl-Abegg Se Impeller for diagonal or centrifugal fans, injection molding tool for producing such an impeller and device with such an impeller
CN106457964B (en) * 2014-06-11 2019-04-02 松下知识产权经营株式会社 Thermostat unit, humidity control system and the vehicle for having thermostat unit
FR3024186A1 (en) * 2014-07-22 2016-01-29 Air Liquide Medical Systems RESPIRATORY ASSISTING APPARATUS WITH MICRO-SUFFLANTING WHEEL MOLDED MONOBLOC
JP6390272B2 (en) * 2014-08-29 2018-09-19 日本電産株式会社 Impeller and blower
USD759227S1 (en) 2014-10-29 2016-06-14 Gentherm Incorporated Cover
WO2016067408A1 (en) * 2014-10-30 2016-05-06 三菱電機株式会社 Air conditioner
CN106337833A (en) * 2015-07-06 2017-01-18 杭州三花研究院有限公司 Impeller, centrifugal pump and electric drive pump
US10644363B2 (en) * 2015-09-14 2020-05-05 Panasonic Intellectual Property Management Co., Ltd. Temperature conditioning unit, temperature conditioning system, and vehicle
DE102015117470A1 (en) * 2015-10-14 2017-04-20 Atlas Copco Energas Gmbh Turbine wheel for a radial turbine
DE102015117463A1 (en) * 2015-10-14 2017-04-20 Atlas Copco Energas Gmbh Turbine wheel for a radial turbine
CN105570192B (en) * 2016-02-29 2018-08-17 李锦标 A kind of draught fan impeller and its processing method
DE102016113589A1 (en) 2016-07-22 2018-01-25 Ebm-Papst Landshut Gmbh blower
JP6775379B2 (en) * 2016-10-21 2020-10-28 三菱重工業株式会社 Impeller and rotating machine
DE102017114682A1 (en) * 2017-02-23 2018-08-23 Ebm-Papst Landshut Gmbh One-piece impeller
EP3530956B1 (en) 2018-02-26 2021-09-22 Honeywell Technologies Sarl Impeller for a radial fan and gas burner appliance
CN109185226A (en) * 2018-10-24 2019-01-11 佛山市启正电气有限公司 Ceiling fan and its flabellum
US10939849B2 (en) * 2018-10-31 2021-03-09 Monitored Therapeutics, Inc Low flow spirometer turbine
US11218048B2 (en) 2018-12-14 2022-01-04 Nidec Motor Corporation Shaft-mounted slinger for electric motor
TWI775036B (en) * 2020-01-14 2022-08-21 宏碁股份有限公司 Heat dissipation fan
CN113250978A (en) * 2020-02-11 2021-08-13 宏碁股份有限公司 Heat radiation fan
US11473232B2 (en) * 2020-12-09 2022-10-18 Haier Us Appliance Solutions, Inc. Motor assembly for a washing machine appliance
CN114233680A (en) * 2021-12-29 2022-03-25 续新电器技术(深圳)有限公司 Combined type fan blade and combined air outlet device
CN217080873U (en) * 2022-03-04 2022-07-29 台达电子工业股份有限公司 Impeller

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE441359C (en) 1924-11-06 1927-03-02 Fuller Lehigh Company Shaft dryer for coal u. like
CH301116A (en) 1952-05-27 1954-08-31 Ag Hch Bertrams Fan pressure casing.
US3224079A (en) * 1964-12-28 1965-12-21 Ruth D Mayne Method for manufacture of turbine type blower wheels
SE309082B (en) 1965-07-15 1969-03-10 Bahco Ab
DE1557138B2 (en) * 1966-02-10 1973-08-23 Metallgesellschaft AG, 6000 Frank fürt DEVICE FOR GASIFYING LIQUIDS
US3788765A (en) * 1971-11-18 1974-01-29 Laval Turbine Low specific speed compressor
GB1416882A (en) * 1972-03-01 1975-12-10 Hotpoint Ltd Tumbler type dryers
US3865506A (en) 1973-07-09 1975-02-11 Micro Gen Equipment Corp Centrifugal compressor
DE2556824A1 (en) 1975-12-17 1977-06-30 Webasto Werk Baier Kg W FAN WHEEL, IN PARTICULAR HEATING AIR FAN WHEEL FOR A VEHICLE HEATER
US4900228A (en) * 1989-02-14 1990-02-13 Airflow Research And Manufacturing Corporation Centrifugal fan with variably cambered blades
DE3924281A1 (en) 1989-07-22 1991-01-31 Standard Elektrik Lorenz Ag DEVICE FOR CONVEYING A GASEOUS MEDIUM
DE4141359A1 (en) 1991-12-14 1993-06-17 Sel Alcatel Ag Impeller for radial-flow fan - Has numerous apertures in surface of impeller underside opposite to impeller suction aperture.
DE4204531A1 (en) 1992-02-15 1993-08-19 Pvs Kunststofftechnik Gmbh & C Air ventilator, esp. radial type - has vanes connected to hub fitting central shaft by elastic mountings
US6139274A (en) * 1998-08-06 2000-10-31 Tcg Unitech Aktiengesellschaft Radial impeller for a centrifugal pump
US6249071B1 (en) * 1998-10-14 2001-06-19 Advanced Rotary Systems Llc Rotor drive motor with u-shaped stator cores
US6224335B1 (en) * 1999-08-27 2001-05-01 Delphi Technologies, Inc. Automotive air conditioning fan assembly
US6280143B1 (en) 1999-11-30 2001-08-28 Fantom Technologies Inc. Blade for fluid pump
FR2807117B1 (en) 2000-03-30 2002-12-13 Technofan CENTRIFUGAL FAN AND BREATHING ASSISTANCE DEVICE COMPRISING SAME
KR100355827B1 (en) * 2000-08-17 2002-11-07 엘지전자 주식회사 Turbo fan of Window type Air conditioner
KR100818429B1 (en) 2000-12-04 2008-04-01 로버트 보쉬 코포레이션 High efficiency one-piece centrifugal blower
KR100405981B1 (en) * 2001-02-12 2003-11-14 엘지전자 주식회사 Structure of turbo fan for cassette type air conditioner
US6848887B2 (en) * 2001-08-23 2005-02-01 Lg Electronics Inc. Turbofan and mold thereof
JP2003090298A (en) * 2001-09-17 2003-03-28 Nippon Soken Inc Centrifugal fan
DE10204037C5 (en) 2002-02-01 2009-07-23 Ebm-Papst Landshut Gmbh Radial fan with electric motor
KR20040104974A (en) * 2003-06-03 2004-12-14 삼성전자주식회사 Turbofan and mold for manufacturing the same
KR100574860B1 (en) * 2004-02-25 2006-04-27 엘지전자 주식회사 The fan structure of air-conditioner inner door unit
US7165938B2 (en) * 2004-09-20 2007-01-23 Sen-Yung Lee Fan device for removing heat from heat sources

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022003842A1 (en) 2021-10-19 2023-04-20 Truma Gerätetechnik GmbH & Co. KG impeller

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US20100098544A1 (en) 2010-04-22
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US20080292464A1 (en) 2008-11-27
EP2196679A2 (en) 2010-06-16
US8109731B2 (en) 2012-02-07
WO2006013067A3 (en) 2006-12-28
ATE544953T1 (en) 2012-02-15
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EP1774180A2 (en) 2007-04-18
WO2006013067A2 (en) 2006-02-09

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