EP3273066B1 - Roue de ventilateur - Google Patents

Roue de ventilateur Download PDF

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Publication number
EP3273066B1
EP3273066B1 EP17180706.8A EP17180706A EP3273066B1 EP 3273066 B1 EP3273066 B1 EP 3273066B1 EP 17180706 A EP17180706 A EP 17180706A EP 3273066 B1 EP3273066 B1 EP 3273066B1
Authority
EP
European Patent Office
Prior art keywords
impeller
blade
impeller blades
radially
support plate
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
EP17180706.8A
Other languages
German (de)
English (en)
Other versions
EP3273066A1 (fr
Inventor
Tobias Schmidt
Roland Keber
Jan Kopper
Martin DEININGER
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
Publication of EP3273066A1 publication Critical patent/EP3273066A1/fr
Application granted granted Critical
Publication of EP3273066B1 publication Critical patent/EP3273066B1/fr
Active legal-status Critical Current
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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
    • F04D29/26—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
    • F04D29/30—Vanes
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade

Definitions

  • the invention relates to an impeller with a cover disk and a support disk and a large number of impeller blades arranged between the cover disk and the support disk and distributed over the circumference of the impeller.
  • the impeller is primarily designed as a radial impeller and used in radial fans.
  • the known impellers work very well in practice and achieve a high level of efficiency with little noise.
  • the requirements to the impellers are constantly increasing in this regard, so that it is the object of the invention to further develop the known impellers in such a way that an even more efficient conveyance of air/gases or gas mixtures can be achieved with low production costs.
  • an impeller is proposed with a cover disk and a support disk and a large number of impeller blades arranged between the cover disk and the support disk and distributed over the circumference of the impeller, with a hub being formed on the support disk on an axis of rotation of the impeller and the cover disk rotating around the axis of rotation having extending axial inlet port.
  • the impeller blades each have a blade section ending radially on the inside, in which the blade edges are curved at least in sections and extend in the axial direction up to the support disk.
  • the hub disk forms a radially extending blade edge lap portion in which the axial end edges of the impeller blades abut the hub disk, with an overall radial length of the blade edge lap portion being less than that of the individual impeller blades.
  • the at least partially arcuate blade sections of the impeller blades which end radially inwards, are located in the region of the inlet opening and the flow flows directly against them when the impeller is in operation.
  • the combination of this geometric shape of the radially inwardly ending at least partially arcuate blade sections with the radial blade edge overlap section of the support disk that is shortened compared to the radial length of the individual impeller blades increases the aerodynamic efficiency by reducing the flow losses measurably increased compared to the impellers known from the prior art.
  • the blade edges of the impeller blades are each exposed in the blade section ending radially on the inside and are uncovered by the cover disk. After entering through the inlet opening, the flow therefore directly hits the specially shaped blade sections of the impeller blades, which end radially inwards, and whose curved section is bent convexly inwards.
  • all impeller blades are curved forwards or backwards and are identical in shape.
  • the impeller is characterized in that the diameter of the section of the support disk adjoining the axis of rotation is smaller than the diameter of the inlet opening of the cover disk. In an axial plan view of the inlet opening, the peripheral edge of this section of the support disk can thus be seen.
  • the impeller is advantageously designed in one piece.
  • the preferred material is plastic.
  • the impeller blades have a blade edge portion adjoining the cover plate in the blade section ending radially inward in each case, in which the blade edges run at least in sections in an arc shape, in which the blade edges run radially in a straight line when viewed in a lateral cross section.
  • the impeller blades have a blade edge portion adjoining the support disk in the blade section ending radially inward in each case, in which the blade edges run in an arc at least in sections, in which the blade edges run axially in a straight line when viewed in a lateral cross section.
  • the impeller blades have a blade edge portion adjoining the cover plate in the blade section ending radially inward in each case, in which the blade edges run at least in sections in an arc shape, in which the blade edges in a lateral cross section are straight at an angle to a radial plane run, which is greater than zero, preferably in a range of 10 - 30 °.
  • one embodiment provides that the impeller blades have a blade edge portion adjoining the support disk in the blade section ending radially inward in each case, in which the blade edges are at least partially arcuate, in which the blade edges in a lateral cross section are straight in extend at an angle to an axial plane which is greater than zero, preferably in a range of 10-30°.
  • the impeller blades therefore always have an arcuate, inwardly directed convex portion in the blade portion ending radially inward, which either directly adjoins the support disk and/or the cover disk.
  • a blade edge section adjoining the support disk and/or the cover disk is additionally provided, which extends between the arcuate section and the support disk and/or cover disk.
  • the blade edge section adjoining the support disk runs in a straight line, parallel or inclined to the axis of rotation or an axial plane.
  • the blade edge section adjoining the cover disk runs in a straight line, parallel or inclined to a radial plane.
  • the length F1 of the running blade edge section in relation to a maximum axial height b1 of the impeller blades in the respective radially inwardly ending blade section is in a range that applies 0 ⁇ F1/b1 ⁇ 0.75.
  • a length F2 of the straight blade edge section adjoining the support disk is in a range in relation to a maximum axial height b1 of the impeller blades in the blade section ending radially inward in each case, such that 0 ⁇ F2/b1 ⁇ 0.75 applies.
  • the curved section of the blade edges of the blade section ending radially on the inside in each case extends up to the cover disk and/or the support disk. In that case, blade edge sections running in a straight line are dispensed with.
  • the ratio between the maximum axial height b1 of the impeller blades and the maximum height H1 between the edge of the inlet opening and the axial inner surface of the support disk is in a range that applies 0.6 ⁇ b1/H1 ⁇ 0.9.
  • the ratio between a length A1, over which the impeller blades rest on a section of the support disk adjoining the axis of rotation, and the impeller diameter D is in a range that applies 0.02 ⁇ A1/D ⁇ 0.25. If the impeller blades run in a straight line, the length A1 corresponds to a straight line; in the case of curved impeller blades, the length A1 is determined via the line integral.
  • the impeller blades according to the invention have a connection section to the cover disk , wherein the connection section has a width t2 in an axial plan view cut radially through the blade and the impeller blades have a width t1 in an axial plan view in the blade section ending radially inwards, and with regard to the ratio of the widths, 0.16 ⁇ t1/t2 ⁇ 0 applies ,8th.
  • the support disk has a ring which is spaced apart in the radial direction and adjoins a section of the support disk adjoining the axis of rotation, the axial end edges of the impeller blades bearing against the ring of the support disk and being axially covered by it.
  • the ring forms a proportion of the total radial length of the blade edge lap portion. The distance from the radially inner section of the support disk ensures that the axial blade edges are not covered by the support disk, at least in sections, in order to achieve the fluidic advantages according to the invention.
  • the ring is arranged on the radial outer edge of the fan wheel blades and terminates flush with an axially adjacent radial outer edge of the fan wheel blades.
  • the impeller is designed in such a way that the impeller blades extend in the radial direction beyond the cover disk.
  • impeller In a further development of the impeller, provision is also made for it to have radially shorter intermediate blades, which are attached exclusively to the cover disk and the ring.
  • an embodiment variant of the impeller is also advantageous in which the impeller blades, seen in an axial top view, extend tangentially to a circular plane around the axis of rotation in the blade section ending radially on the inside.
  • an axial plan view and side sectional views AA and BB show an exemplary embodiment of a one-piece radial impeller 1 with a cover disk 2 that is curved in cross-section, a support disk 3 and a large number between the cover disk 2 and the support disk 3 distributed over the circumference of the impeller 1 arranged fan wheel blades 4 shown.
  • the impeller 1 has in the Cover plate 2 has an axial inlet opening 6 for sucking in air and/or gas mixtures.
  • the outlet 25 for blowing out the air and/or the gas mixtures is located on the radial outside of the impeller 1 .
  • the support disk 3 extends radially outwards around the central axis of rotation in a convex manner in the axial direction and forms the hub 5 of the impeller 1 outer spaced portion of the support disk.
  • the impeller blades 4 each have a blade section 7 ending radially on the inside, in which the blade edges 8 are curved in sections and extend in the axial direction up to the support disk 3 and merge into it in one piece.
  • the support disk 3 forms with the ring 16 a blade edge overlapping section 9 extending in the radial direction, in which the axial end edges of the impeller blades 4 are each covered by the support disk 3 and are connected to it in one piece.
  • the total radial length of the blade edge lap portion 9 is less than that of the individual impeller blades 4, so that the axial blade edges are uncovered and exposed in the axial direction in all portions where neither the supporting disk 3 nor the ring 16 are formed.
  • the impeller blades 4 run tangentially to an imaginary circular plane about the axis of rotation.
  • intermediate blades 24 are provided, which are exclusively connected to the ring 16 and the cover disk 2 .
  • the intermediate blades 24 are spaced with their radially inner edge portion from a radial outer edge of the radially outwardly extending portion of the hub 5 of the support disk 3 .
  • the impeller blades 4 comprise a connection section 15 to the cover disk 2, in which their width t2 is greater than in the blade section 7 ending radially on the inside, in which they have a width t1.
  • the ratio of t1/t2 has the value 0.6 in the embodiment shown.
  • the connection section 15 extends radially outwards over the entire length of the impeller blade 4 along the cover plate 2.
  • FIG. 4a - 4c three alternative exemplary embodiments of the blade edges 8 in the blade section 7 ending radially on the inside are shown.
  • the blade edges 8 of the impeller blades 4 have three blade edge sections in the blade section 7 ending radially inwards.
  • the blade edge portion 13 immediately adjoining the blade edge portion 10 is arcuate and convex radially inward, with its arcuate shape having a constant rounding.
  • the variant according to Figure 4b is identical to the one from Figure 4a except that the two blade edge portions 10 and 11 radially or extend axially in a straight line parallel to the imaginary radial plane or axial plane.
  • the ratio of the length F2 of the straight blade edge section 11 adjoining the support disk 3 to the maximum axial height b1 of the fan wheel blades 4 in the blade section 7 ending radially inward is at a value of 0.25 ( Figure 4a ) or 0.3 ( Figure 4b ).
  • the maximum height b1 determines the flow entry height from the support disk 3 into the radially adjoining impeller section with exposed axial blade edges.
  • the arcuate, convex blade edge section 13 follows directly on the support disk 3 .
  • the rounding of the arc-shaped convex blade edge portion 13 is less than in the embodiments according to FIG Figures 4a and 4b .

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

Claims (14)

  1. Roue de ventilateur, comprenant un disque de couverture (2) et un disque de support (3) ainsi qu'une pluralité de pales de roue de ventilateur (4) réparties sur la circonférence de la roue de ventilateur entre le disque de couverture (2) et le disque de support (3), dans laquelle un moyeu (5) est réalisé sur le disque de support (3) au niveau d'un axe de rotation de la roue de ventilateur (1), et le disque de couverture (2) présente une ouverture d'entrée axiale (6) s'étendant autour de l'axe de rotation, les pales de roue de ventilateur (4) présentant respectivement une section de pale (7) se terminant radialement à l'intérieur dans laquelle les bords de pale (8) s'étendent en forme d'arc au moins par endroits et s'étendent dans la direction axiale jusqu'au disque de support (3), le disque de support (3) formant une section de recouvrement de bord de pale (9) s'étendant dans la direction radiale dans laquelle les bords d'attaque axiaux des pales de roue de ventilateur (4) sont adjacents au disque de support (3), une longueur radiale totale de la section de recouvrement de bord de pale (9) étant inférieure à celle des pales de roue de ventilateur (4) individuelles,
    caractérisée en ce que les pales de roue de ventilateur (4) présentent une section de liaison (15) avec le disque de couverture (2), la section de liaison (15) présentant en vue de dessus axiale une largeur une largeur t2, et les pales de roue de ventilateur (4) présentant en vue de dessus axiale, dans la section de pale (7) se terminant radialement à l'intérieur, une largeur t1, soit un rapport entre les largeurs de 0,16 ≤ t1/t2 ≤ 0,8.
  2. Roue de ventilateur selon la revendication 1, caractérisée en ce que les bords de pale des pales de roue de ventilateur (4) sont respectivement exposés dans la section de pale (7) se terminant radialement à l'intérieur et ne sont pas recouverts par le disque de couverture (2).
  3. Roue de ventilateur selon la revendication 1 ou 2, caractérisée en ce qu'un diamètre (D1) d'une section du disque de support (3) se raccordant à l'axe de rotation est inférieur à un diamètre (D2) de l'ouverture d'entrée du disque de couverture (2).
  4. Roue de ventilateur selon l'une quelconque des revendications précédentes 1 à 3, caractérisée en ce que les pales de roue de ventilateur (4) dans la section de pale (7) se terminant respectivement radialement à l'intérieur, dans laquelle les bords de pale s'étendent en forme d'arc au moins par endroits, présentent une section de bord de pale (10) adjacente au disque de couverture (2) dans laquelle les bords de pale s'étendent radialement en ligne droite, vus en section transversale latérale.
  5. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que les pales de roue de ventilateur (4) dans la section de pale (7) se terminant respectivement radialement à l'intérieur, dans laquelle les bords de pale s'étendent en forme d'arc au moins par endroits, présentent une section de bord de pale (11) adjacente au disque de support (3), dans laquelle les bords de pale s'étendent axialement en ligne droite, vus en section transversale latérale.
  6. Roue de ventilateur selon l'une quelconque des revendications précédentes 1 à 3, caractérisée en ce que les pales de roue de ventilateur (4) dans la section de pale (7) se terminant respectivement radialement à l'intérieur, dans laquelle les bords de pale s'étendent en forme d'arc au moins par endroits, présentent une section de bord de pale (10) adjacente au disque de couverture (2), dans laquelle les bords de pale s'étendent en section transversale latérale en ligne droite selon un angle (α) supérieur à zéro par rapport à un plan radial.
  7. Roue de ventilateur selon l'une quelconque des revendications précédentes 1 à 3 et 6, caractérisée en ce que les pales de roue de ventilateur (4) dans la section de pale (7) se terminant respectivement radialement à l'intérieur, dans laquelle les bords de pale s'étendent en forme d'arc au moins par endroits, présentent une section de bord de pale (11) adjacente au disque de support (3), dans laquelle les bords de pale en section transversale latérale s'étendent en ligne droite selon un angle (β) supérieur à zéro par rapport à un plan axial.
  8. Roue de ventilateur selon l'une quelconque des revendications précédentes 4 à 7, caractérisée en ce qu'une longueur F1 de la section de bord de pale (10) s'étendant en ligne droite, adjacente au disque de couverture (2), se situe par rapport à une hauteur axiale maximale b1 des pales de roue de ventilateur (4) dans la section de pale (7) se terminant respectivement radialement à l'intérieur dans une plage telle que 0 < F1/b1 ≤ 0,75.
  9. Roue de ventilateur selon l'une quelconque des revendications précédentes 4 à 8, caractérisée en ce qu'une longueur F2 de la section de bord de pale (11) s'étendant en ligne droite, adjacente au disque de support (3), se situe par rapport à une hauteur axiale maximale b1 des pales de roue de ventilateur (4) dans la section de pale se terminant respectivement radialement à l'intérieur dans une plage telle que 0 < F2/b1 ≤ 0,75.
  10. Roue de ventilateur selon l'une quelconque des revendications précédentes 1 à 3, caractérisée en ce que la section (13) s'étendant respectivement en forme d'arc des bords de pale de la section de pale (7) se terminant respectivement radialement à l'intérieur s'étend jusqu'au disque de couverture (2) et/ou au disque de support (3).
  11. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rapport entre une hauteur axiale maximale b1 des pales de roue de ventilateur (4) et une hauteur maximale H1 entre un rebord d'ouverture d'entrée (14) et la surface intérieure axiale du disque de support (3) se situe dans une plage telle que 0,6 ≤ b1/H1 ≤ 0,9, et/ou en ce qu'un rapport entre une longueur A1 sur laquelle les pales de roue de ventilateur (4) sont appliquées contre une section se raccordant à l'axe de rotation du disque de support (3) et le diamètre de roue de ventilateur D se situe dans une plage telle que 0,02 ≤ A1/D ≤ 0,25.
  12. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de support (3) présente une bague (16) qui se raccorde dans la direction radiale à distance d'une section du disque de support (3) se raccordant à l'axe de rotation, dans laquelle les bords d'attaque axiaux des pales de roue de ventilateur (4) s'appliquent contre la bague (16) du disque de support (3) et sont recouvertes axialement par celle-ci, et la bague (16) faisant partie de la longueur radiale totale de la section de recouvrement de bord de pale (9).
  13. Roue de ventilateur selon la revendication précédente, caractérisée en ce que la bague (16) est disposée sur le bord extérieur radial des pales de roue de ventilateur (4), et/ou les pales de roue de ventilateur (4) s'étendent dans la direction radiale au-delà du disque de couverture (2).
  14. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que les pales de roue de ventilateur (4), en vue de dessus axiale, s'étendent dans la section de pale (7) se terminant radialement à l'intérieur tangentiellement par rapport à un plan de cercle autour de l'axe de rotation, et/ou en ce qu'elle présente des pales intermédiaires radialement plus courtes qui ne sont fixées qu'au disque de couverture (2) et à la bague (16).
EP17180706.8A 2016-07-22 2017-07-11 Roue de ventilateur Active EP3273066B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016113589.5A DE102016113589A1 (de) 2016-07-22 2016-07-22 Gebläserad

Publications (2)

Publication Number Publication Date
EP3273066A1 EP3273066A1 (fr) 2018-01-24
EP3273066B1 true EP3273066B1 (fr) 2022-06-15

Family

ID=59315484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17180706.8A Active EP3273066B1 (fr) 2016-07-22 2017-07-11 Roue de ventilateur

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Country Link
EP (1) EP3273066B1 (fr)
CN (1) CN207178292U (fr)
DE (2) DE102016113589A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202017103925U1 (de) * 2017-02-23 2017-07-20 Ebm-Papst Landshut Gmbh Einstückiges Gebläserad
EP3530956B1 (fr) 2018-02-26 2021-09-22 Honeywell Technologies Sarl Roue à aubes pour soufflante radiale et appareil à brûleur à gaz

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4318580A1 (de) * 1993-06-04 1994-12-08 Sel Alcatel Ag Radialgebläse
DE202004012015U1 (de) 2004-07-31 2005-12-22 Ebm-Papst Landshut Gmbh Radialgebläserad
EP2058525B1 (fr) * 2007-11-12 2010-04-28 Elica S.P.A. Turbine de ventilateur radial et ventilateur radial
KR101833935B1 (ko) * 2011-02-22 2018-03-05 삼성전자주식회사 공기조화기의 터보팬

Also Published As

Publication number Publication date
CN207178292U (zh) 2018-04-03
DE202017103890U1 (de) 2017-07-21
EP3273066A1 (fr) 2018-01-24
DE102016113589A1 (de) 2018-01-25

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