EP3916239B1 - Roue de soufflerie pourvu de pales de rotor courbées tridimensionnelles - Google Patents

Roue de soufflerie pourvu de pales de rotor courbées tridimensionnelles Download PDF

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Publication number
EP3916239B1
EP3916239B1 EP21172988.4A EP21172988A EP3916239B1 EP 3916239 B1 EP3916239 B1 EP 3916239B1 EP 21172988 A EP21172988 A EP 21172988A EP 3916239 B1 EP3916239 B1 EP 3916239B1
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EP
European Patent Office
Prior art keywords
section
fan wheel
impeller blades
blade
wheel according
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
EP21172988.4A
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German (de)
English (en)
Other versions
EP3916239A1 (fr
Inventor
Daniel Gebert
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 Mulfingen GmbH and Co KG
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Ebm Papst Mulfingen GmbH and Co KG
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Publication of EP3916239A1 publication Critical patent/EP3916239A1/fr
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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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved

Definitions

  • the invention relates to a fan wheel with three-dimensionally curved impeller blades.
  • blower wheels with impeller blades curved forward or backward relative to the direction of rotation and impeller blades curved relative to the axis of rotation of the blower wheel are known, for example from the publication DE 10 2017 114 679 A1 . Further state of the art in the present technical field is, for example, in the publications EP 2 275 689 A1 , EP 2 921 711 A1 , EP 2 910 793 A1 and US 2014/062232 A1 disclosed.
  • blower wheel presented here is used for elements that conduct volume flow, for example so-called air handling units, in the field of ventilation and air conditioning technology.
  • Strength and especially speed stability play a crucial role.
  • a critical point is this Material stress at the transition between the respective impeller blade of the fan wheel and the base disk and/or the cover disk.
  • radii are often provided in the transition area in the prior art.
  • the invention is based on the object of further optimizing the previous solutions for the fan wheels with regard to their efficiency, noise development and the possibility of even higher speeds.
  • a fan wheel is proposed with a base disk, a cover disk and impeller blades arranged around a rotation axis of the fan wheel, each of which extends over a blade length from a blade leading edge to a blade trailing edge.
  • the impeller blades are divided into a front section, which extends from the front edge of the blade towards the rear edge of the blade, a rear section which extends from the rear edge of the blade towards the front edge of the blade, and a transition section which forms a transition between the front section and the rear section .
  • the impeller blades in the front section and the rear section are designed to be curved in opposite directions in the course from the bottom disk to the cover disk.
  • the invention is further characterized in that the impeller blades in the front section and the rear section are designed to be opposite, in particular three-dimensionally curved, compared to a shortest connection between the base disk and the cover disk.
  • the impeller blades are curved in an arc shape.
  • the arc is preferably drawn at one constant or substantially constant arc radius.
  • a design of the fan wheel in which the front section extends over at least 5%, preferably over 10-40% of the blade length is also advantageous.
  • the rear section extends over at least 5%, preferably over 10-40% of the blade length.
  • the transition section connects the front section and the rear section.
  • the transition takes place in a continuous course along the blade length.
  • the change in the curvature of the front section and the rear section i.e. the opposite curvature in the front section and the rear section, is preferably achieved in the transition section by a uniform course.
  • the design of the impeller according to the invention which is advantageous in terms of flow technology provides that the front section is curved towards the axis of rotation and the rear section is curved away from the axis of rotation.
  • the base disk also preferably has a hub on which the impeller blades are attached or formed.
  • the hub forms an interface to the motor and is either formed in one piece by the base disk or arranged on it.
  • the fan wheel has the cover disk, which covers the axial blade end edges of the impeller blades at least in sections, in particular completely.
  • the cover plate then forms the axial suction opening of the fan wheel.
  • a further development of the fan wheel is characterized in that the impeller blades end radially inwards on the base disk at a distance (R) relative to an outer radius of the base disk, which is at least 5% of a total diameter (D) of the base disk is determined, so that R/D>0.05, a more preferred range is between 5-25%, more preferably between 10-15%.
  • the impeller blades therefore end clearly set back from the radial outer edge of the base disk, so that the flow rests on the base disk over a longer distance.
  • the impeller is characterized in that the base disk has an elliptical cross section on its radial outer edge section, so that its radial outer edge runs parallel or essentially parallel to the axis of rotation.
  • the cover disk also has a radially inner section which determines an axial extension parallel to the axis of rotation.
  • the impeller blades do not rest on the axially extending section.
  • the cover disk then extends further in a particularly radial direction and extends over the impeller blades while lying against it.
  • an embodiment of the cover disk is advantageous in which, viewed in a lateral cross section, it has a curved course at least in sections and determines an axial change of direction at its radial outer edge section.
  • the impeller blades extend from the front edge of the blade to the rear edge of the blade in each case radially outwards and around the axis of rotation.
  • the impeller blades are therefore curved forward or backward in relation to the direction of rotation.
  • the blower wheel according to the invention is designed in particular as a radial impeller or diagonal impeller.
  • the impeller is preferably made in one piece, in particular made of plastic.
  • impellers made of metal, especially sheet metal, are also possible.
  • FIGS. 1 and 2 show perspective views of the blower wheel 1 in an embodiment as a one-piece radial impeller with a base disk 4, a cover disk 3 defining the suction opening 25 and impeller blades 2 arranged backwardly curved between the base disk 4 and the cover disk 3 in a blade ring around the rotation axis RA.
  • the impeller blades 2 run from a hub 9 formed by the base disk 4 from their inlet-side blade leading edge 5 in the circumferential direction and radially outwards to their outlet-side blade rear edge 6.
  • the cover disk 3 completely extends over the axial end edges of the impeller blades 2. During operation the flow is axial through the suction opening 25 sucked in and blown out radially through the channels formed between the impeller blades 2.
  • each of the impeller blades 2 has three sections, namely the front section 10, which extends from the blade front edge 5 in the direction of the blade rear edge 6, the rear section 12, which extends from the blade rear edge 6 in Direction of the blade leading edge 5 extends, and the transition section 11, which forms the transition between the front section 10 and the rear section 12.
  • the front section 10 is through the cut in Figure 3 , the rear section through the cut in Figure 4 clearly visible.
  • the impeller blades 2 are curved in a three-dimensional arc in the direction from the base disk 4 to the cover disk 3 in the opposite direction to the axis of rotation RA.
  • the shortest connection between the base plate 4 and the cover plate 3 is indicated by the straight line 8, 8 ', so that the curvature can be better understood.
  • the arcuate curvature occurs in such a way that the impeller blades 2 in the front section 10 and the rear section 12 are designed to be three-dimensionally curved in opposite directions, with the curvature in the exemplary embodiment shown in the front section 10 towards the axis of rotation (see Figure 3 ) and in the rear section 12 away from the axis of rotation (see Figure 4 ) he follows.
  • the curvature towards and away from the rotation axis RA can also be done in reverse.
  • the impeller blades 2 merge into both the base disk 4 and the cover disk 3 at an angle to the axis of rotation. Together with the bottom disk 4, the impeller blades 2 thus form V-shaped connection areas 18, 18 'in the front section 10 and rear section 12 in the lateral cross section, the opening angle between the respective Impeller blade 2 and the bottom disk 4 of the connection area 18 'in the rear section 12 is significantly smaller than that of the connection area 18 in the front section 10.
  • the front section 10 and the rear section 12 each extend over approximately 30% of the entire blade length, the transition section 11 in between determines the rest.
  • the transition section 11 has a continuous course along the blade length, so that the change in direction of the curvature of the impeller blades 2 from the front section 10 to the rear section 12 along the blade length uniformly over the entire axial height of the impeller blades 2 and without jump.
  • FIG. 1 shows the distance R between the blade rear edge 6 and the outer radius of the base disk 4.
  • both the cover disk 3 and the bottom disk 4 are specially shaped.
  • the cover disk 3 initially has the section 21, which extends axially parallel to the axis of rotation RA and determines the suction opening 25. Seen in the lateral cross section, this is followed by an arcuately curved course that covers the impeller blades 2 and, like a winglet, merges back into the axial direction parallel to the rotation axis RA in the radial outer edge section 23.
  • the cover disk 3 therefore carries out a complete axial change of direction over its radial extent.
  • the outer edge section 23 lies adjacent to the impeller blades 2, as shown in Figure 4 can be recognized.
  • the bottom disk 4 has an elliptical cross section at its radial outer edge section 22 and goes from an extension radially outward into an axial extension so that the radial outer edge of the bottom disk 4 runs parallel or substantially parallel to the axis of rotation RA.
  • base disks and/or cover disks can also be used.

Landscapes

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

Claims (13)

  1. Roue de ventilateur (1), comprenant un disque de fond (4), un disque de recouvrement (3) et des pales de roue (2) disposées autour d'un axe de rotation (RA) de la roue de ventilateur et qui s'étendent respectivement sur une longueur de pale d'un bord d'attaque de pale (5) à un bord de fuite de pale (4), dans laquelle les pales de roue (2) sont divisées en une partie avant (10) qui s'étend en partant du bord d'attaque de pale (5) en direction du bord de fuite de pale (6), en une partie arrière (12) qui s'étend en partant du bord de fuite de pale (6) en direction du bord d'attaque de pale (5), et en une partie de transition (11) qui constitue une transition entre la partie avant (10) et la partie arrière (12), et dans laquelle les pales de roue (2) sont réalisées avec une courbure opposée sur le tracé du disque de fond (4) au disque de recouvrement (3) dans la partie avant (10) et la partie arrière (12),
    caractérisée en ce que les pales de roue (2) sont réalisées avec une courbure opposée dans la partie avant (10) et la partie arrière (12) par rapport à un raccordement le plus court entre le disque de fond (4) et le disque de recouvrement (3), et en ce que la partie avant (10) est réalisée de manière courbée vers l'axe de rotation (RA), et la partie arrière (12) est réalisée de manière courbée en s'éloignant de l'axe de rotation (RA).
  2. Roue de ventilateur selon la revendication 1, caractérisée en ce que les pales de roue (2) sont réalisées de manière courbée en arc.
  3. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que la partie avant (10) s'étend sur au moins 5 %, en particulier sur 10 à 40 %, de la longueur de pale.
  4. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que la partie arrière (12) s'étend sur au moins 5 %, en particulier sur 10 à 40 %, de la longueur de pale.
  5. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que la partie de transition (11) présente un tracé constant le long de la longueur de pale.
  6. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de fond (4) présente ou réalise un moyeu (9) de la roue de ventilateur (1) qui constitue une interface avec un moteur et sur lequel les pales de roue (2) sont fixées ou réalisées.
  7. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de recouvrement (3) recouvre par endroits, en particulier complètement, des bords frontaux de pale axiaux des pales de roue (2).
  8. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que les pales de roue (2) se terminent par rapport à un rayon extérieur du disque de fond (4) radialement vers l'intérieur à une distance (R) au niveau du disque de fond (4) qui détermine au moins 5 % d'un diamètre total (D) du disque fond, en particulier de 5 à 25 %, et de préférence de 10 à 15 %, de sorte que R/D > 0,05, en particulier 0,05 ≤ R/D ≤ 0,25, et de préférence 0,10 ≤ R/D ≤ 0,15.
  9. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de fond (4) présente au niveau de sa partie radiale de bord extérieur (22) une section transversale elliptique de sorte que son bord extérieur radial s'étend en parallèle ou substantiellement en parallèle à l'axe de rotation (RA).
  10. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de recouvrement (3) présente une partie (21) située radialement à l'intérieur qui présente une étendue axiale parallèle ou substantiellement parallèle à l'axe de rotation (RA).
  11. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que le disque de recouvrement (3), vu en section transversale latérale, présente un tracé courbe, et détermine au niveau de sa partie radiale de bord extérieur (23) un changement de sens axial.
  12. Roue de ventilateur selon l'une quelconque des revendications précédentes, caractérisée en ce que les pales de roue (2) s'étendent du bord d'attaque de pale (5) au bord de fuite de pale (6) respectivement radialement vers l'extérieur et autour de l'axe de rotation (RA).
  13. Roue de ventilateur selon l'une quelconque des revendications précédentes, réalisée sous la forme d'une roue radiale ou d'une roue diagonale d'une seule pièce.
EP21172988.4A 2020-05-28 2021-05-10 Roue de soufflerie pourvu de pales de rotor courbées tridimensionnelles Active EP3916239B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020114387.7A DE102020114387A1 (de) 2020-05-28 2020-05-28 Gebläserad mit dreidimensional gekrümmten Laufradschaufeln

Publications (2)

Publication Number Publication Date
EP3916239A1 EP3916239A1 (fr) 2021-12-01
EP3916239B1 true EP3916239B1 (fr) 2024-03-13

Family

ID=75887892

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21172988.4A Active EP3916239B1 (fr) 2020-05-28 2021-05-10 Roue de soufflerie pourvu de pales de rotor courbées tridimensionnelles

Country Status (4)

Country Link
US (1) US11506220B2 (fr)
EP (1) EP3916239B1 (fr)
CN (1) CN113738697A (fr)
DE (1) DE102020114387A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD949315S1 (en) * 2016-06-24 2022-04-19 Ebm-Papst Mulfingen Gmbh & Co. Kg Vane damper with trailing edge
WO2021118208A1 (fr) * 2019-12-09 2021-06-17 엘지전자 주식회사 Soufflante
CN117345686B (zh) * 2023-12-06 2024-04-02 泛仕达机电股份有限公司 一种三元扭曲叶片的风扇叶轮及风机

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3482668B2 (ja) * 1993-10-18 2003-12-22 株式会社日立製作所 遠心形流体機械
EP1455094A1 (fr) * 2003-03-04 2004-09-08 Ziehl-Abegg AG Roue ventilateur radial
JP4396775B2 (ja) * 2007-11-26 2010-01-13 ダイキン工業株式会社 遠心ファン
CA2716119C (fr) * 2008-02-22 2017-01-17 Horton, Inc. Appareil ventilateur a flux hybride
KR20100134011A (ko) * 2008-05-14 2010-12-22 다이킨 고교 가부시키가이샤 원심 송풍기
JP4994421B2 (ja) * 2009-05-08 2012-08-08 三菱電機株式会社 遠心ファン及び空気調和機
JP5164932B2 (ja) * 2009-06-11 2013-03-21 三菱電機株式会社 ターボファンおよび空気調和機
US9716420B2 (en) * 2012-08-28 2017-07-25 Regal Beloit America, Inc. Fan and electric machine assembly and methods therefor
WO2014061094A1 (fr) * 2012-10-16 2014-04-24 三菱電機株式会社 Réacteur à double flux et appareil de conditionnement d'air
EP2921711B1 (fr) * 2014-03-21 2020-10-21 punker GmbH Turbine radiale et système de ventilateur
DE102014006756A1 (de) * 2014-05-05 2015-11-05 Ziehl-Abegg Se Laufrad für Diagonal- oder Radialventilatoren, Spritzgusswerkzeug zur Herstellung eines solchen Laufrades sowie Gerät mit einem solchen Laufrad
US10746025B2 (en) * 2016-03-02 2020-08-18 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine wheel, radial turbine, and supercharger
DE102017114679A1 (de) 2017-06-30 2019-01-03 Ebm-Papst Mulfingen Gmbh & Co. Kg Gebläserad

Also Published As

Publication number Publication date
EP3916239A1 (fr) 2021-12-01
US11506220B2 (en) 2022-11-22
US20210372424A1 (en) 2021-12-02
CN113738697A (zh) 2021-12-03
DE102020114387A1 (de) 2021-12-02

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