EP1774180B1 - Roue de soufflante radiale - Google Patents

Roue de soufflante radiale 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
Authority
EP
European Patent Office
Prior art keywords
blades
radial
fan wheel
region
hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP05768016A
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German (de)
English (en)
Other versions
EP1774180A2 (fr
Inventor
Roland Keber
Rudolf Tungl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ebm Papst Landshut GmbH
Original Assignee
Ebm Papst Landshut GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ebm Papst Landshut GmbH filed Critical Ebm Papst Landshut GmbH
Priority to EP10157619.7A priority Critical patent/EP2196679B1/fr
Publication of EP1774180A2 publication Critical patent/EP1774180A2/fr
Application granted granted Critical
Publication of EP1774180B1 publication Critical patent/EP1774180B1/fr
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Anticipated expiration legal-status Critical

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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, 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

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

Claims (10)

  1. Roue de soufflante radiale (1) en particulier pour l'utilisation dans des soufflantes de gaz avec des caractéristiques de soufflante abrupte présentant les propriétés suivantes :
    une pluralité d'aubes (2) disposées réparties sur la périphérie ;
    les aubes (2) s'étendant dans la direction radiale depuis une zone d'entrée interne (4) en direction d'une zone de sortie externe (6) ;
    les aubes (2) s'étendant axialement, c'est-à-dire vue en direction d'un axe rotatif (14), entre une face d'entrée (16) et une face moyeu (18) axialement opposée ;
    les aubes (2) étant reliées sur la face d'entrée (16) par une extension radiale jusqu'à la zone de sortie (6) avec un couvercle de disque (20), qui présente une ouverture d'entrée (22) centrique débouchant dans la zone d'entrée (4) ;
    les aubes (2) et le couvercle de disque (20) définissant un diamètre externe de roue de ventilateur (D) qui est au moins égale à 10 fois une largeur de sortie d'écoulement (B) des aubes (2) existants dans la zone de sortie (6) mesurée axialement,
    caractérisé en ce que les aubes (2) ne sont reliées sur la face de moyeu (18) que par leurs zones d'extrémité radiales internes à un moyeu centrique (24),
    en ce qu'il est prévu des aubes intermédiaires (28) radialement plus courtes qui sont reliées au couvercle de disque (20) dans des zones disposées respectivement entre des aubes voisines (2), aubes qui s'étendent depuis la périphérie externe du couvercle de disque (20) depuis seulement sur une partie de l'extension radiale du couvercle de disque (20) et se terminent à une distance radiale du moyeu (24), et
    les aubes (2) et les aubes intermédiaires (28) étant reliées dans leur zone radialement externe et axialement opposée au couvercle de disque (20) pour renforcer par un élément annulaire circulaire (40).
  2. Roue de soufflante radiale selon la revendication 1,
    caractérisée par une réalisation comme une pièce moulée d'un seul tenant en matière plastique.
  3. Roue de soufflante selon la revendication 1,
    caractérisée en ce que la pièce moulée se compose de matière synthétique comportant des propriétés antistatiques, qui évitent respectivement dévient en cours de fonctionnement des charges statiques.
  4. Roue de soufflante selon l'une des revendications 1 à 2,
    caractérisée en ce que les aubes (2) et/ou les aubes intermédiaires (28) s'étendent dans la direction radiale Incurvée vers l'arrière ou vers l'avant par rapport à la direction de rotation (30).
  5. Roue de soufflante selon l'une des revendications 1 à 3,
    caractérisée en ce que les aubes (2) et/ou les aubes intermédiaires (28) se terminent radialement à la zone de sortie (6).
  6. Roue de soufflante selon l'une des revendications 1 à 4,
    caractérisée en ce que le moyeu (24) se compose d'une section de disque (32) reliée sur sa périphérie externe radiale aux zones d'extrémité internes des aubes (2), tournées vers la zone d'entrée (4) et d'une section de palier (34) centrique à relier à un arbre.
  7. Roue de soufflante selon la revendication 6,
    caractérisé en ce que la section de disque (32) du moyeu (24) est formée eu partant de sa zone périphérique externe reliée aux aubes (2) dans la zone d'entrée (4) et en direction de l'ouverture d'entrée (22) du couvercle de disque (20) de telle sorte que le moyeu (24) forme, sur sa face détournée de l'ouverture d'entrée (22), un espace de logement (36) pour certains éléments de fonction de soufflante tels que des éléments de palier, des pièces de moteur et de rotor et/ou similaires.
  8. Roue de soufflante selon l'une des revendications 1 à 6,
    caractérisée en ce qu'au moins les aubes intermédiaires (28) sont reliées au couvercle de disque (20) par respectivement un renforcement de transition (38).
  9. Roue de soufflante selon l'une des revendications 1 à 8,
    caractérisée en ce que le couvercle de disque (20) présente dans la zone de l'ouverture d'entrée (22) un bord (42) ayant la forme d'une buse dans le sens de l'écoulement.
  10. Roue de soufflante selon l'une des revendications 1 à 8,
    caractérisée en ce qu'une largeur interne d'entrée d'écoulement (C) des aubes (2) est plus large que la largeur de sortie externe d'écoulement (B).
EP05768016A 2004-07-31 2005-07-29 Roue de soufflante radiale Active EP1774180B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10157619.7A EP2196679B1 (fr) 2004-07-31 2005-07-29 Roue pour un ventilateur radiale

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004012015U DE202004012015U1 (de) 2004-07-31 2004-07-31 Radialgebläserad
PCT/EP2005/008250 WO2006013067A2 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP10157619.7A Division EP2196679B1 (fr) 2004-07-31 2005-07-29 Roue pour un ventilateur radiale
EP10157619.7 Division-Into 2010-03-24

Publications (2)

Publication Number Publication Date
EP1774180A2 EP1774180A2 (fr) 2007-04-18
EP1774180B1 true EP1774180B1 (fr) 2012-02-08

Family

ID=35453467

Family Applications (2)

Application Number Title Priority Date Filing Date
EP05768016A Active EP1774180B1 (fr) 2004-07-31 2005-07-29 Roue de soufflante radiale
EP10157619.7A Active EP2196679B1 (fr) 2004-07-31 2005-07-29 Roue pour un ventilateur radiale

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP10157619.7A Active EP2196679B1 (fr) 2004-07-31 2005-07-29 Roue pour un ventilateur radiale

Country Status (5)

Country Link
US (2) US7794206B2 (fr)
EP (2) EP1774180B1 (fr)
AT (1) ATE544953T1 (fr)
DE (1) DE202004012015U1 (fr)
WO (1) WO2006013067A2 (fr)

Cited By (1)

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

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US20100098544A1 (en) 2010-04-22
EP2196679A2 (fr) 2010-06-16
WO2006013067A3 (fr) 2006-12-28
US8109731B2 (en) 2012-02-07
DE202004012015U1 (de) 2005-12-22
EP2196679A3 (fr) 2013-12-18
ATE544953T1 (de) 2012-02-15
US20080292464A1 (en) 2008-11-27
EP1774180A2 (fr) 2007-04-18
EP2196679B1 (fr) 2015-11-25
US7794206B2 (en) 2010-09-14
WO2006013067A2 (fr) 2006-02-09

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