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WO2024110213A1 - Roue diagonale à face de moyeu variable - Google Patents

Roue diagonale à face de moyeu variable Download PDF

Info

Publication number
WO2024110213A1
WO2024110213A1 PCT/EP2023/081400 EP2023081400W WO2024110213A1 WO 2024110213 A1 WO2024110213 A1 WO 2024110213A1 EP 2023081400 W EP2023081400 W EP 2023081400W WO 2024110213 A1 WO2024110213 A1 WO 2024110213A1
Authority
WO
WIPO (PCT)
Prior art keywords
section
hub
blade
blades
diagonal impeller
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.)
Ceased
Application number
PCT/EP2023/081400
Other languages
German (de)
English (en)
Inventor
Daniel Gebert
Niels Blaha
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
Original Assignee
Ebm Papst Mulfingen GmbH and Co KG
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 Mulfingen GmbH and Co KG filed Critical Ebm Papst Mulfingen GmbH and Co KG
Publication of WO2024110213A1 publication Critical patent/WO2024110213A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/06—Helico-centrifugal 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/329—Details of the hub

Definitions

  • the invention relates to a diagonal impeller, the hub of which, together with the blades of the diagonal impeller, defines blade channels, the hub having a changing surface, i.e. a varying hub area, along the flow direction through the blade channel.
  • a diagonal impeller the hub of which, together with the blades of the diagonal impeller, defines blade channels, the hub having a changing surface, i.e. a varying hub area, along the flow direction through the blade channel.
  • a large number of impellers for fans or ventilators are known from the prior art.
  • axial impellers and radial impellers there are also diagonal impellers, as disclosed, for example, in the documents WO 2020/099027 A1 and DE 20 2010 013 785 U1.
  • the fluid to be pumped enters along the impeller axis, i.e. along the axis of rotation on an inflow side, and is blown out again at a certain angle to the axis of rotation on the outflow side, i.e. diagonally.
  • the hub of diagonal impellers is usually completely or purely conical, whereby the formation of vortices in the pumped fluid is to be minimized by the conical shape of the impeller hub.
  • Diagonal impellers also suffer from losses which reduce efficiency and power density. Diagonal impellers also produce noise when operating, which can be annoying depending on the application.
  • the invention is therefore based on the object of overcoming the aforementioned disadvantages and increasing the efficiency and power density of a diagonal impeller as well as improving the noise behavior of a diagonal impeller rotating during operation.
  • a diagonal impeller with a conical hub which can be rotated in particular about a rotation axis, wherein the conical hub widens in the radial direction from an inflow side to an outflow side.
  • a large number of blades extend radially outwards from the hub - as is usual with diagonal impellers.
  • Two immediately adjacent blades of the large number of blades form a blade pair.
  • the blade pair or blade pairs, and more precisely the two blades of the blade pairs, each determine a blade channel through which fluid, for example air or another gas mixture, can flow from the inflow side to the outflow side.
  • the blade channel is delimited radially inwards by a surface of the hub extending between the two blades.
  • the surface of the hub can also be referred to as the hub surface. It is important that the surface of the hub delimiting the blade channel has a first section and a subsequent second section in the flow direction, i.e. from the inflow side to the outflow side, wherein the surface is curved in the first section or has a curvature preferably in the radial direction and is flat in the second section.
  • the surface or the hub surface varies accordingly, so that the hub is in particular not purely or exclusively conical.
  • the plurality of blades forms a plurality of blade pairs, each pair of blades defining a blade channel between them. This results in a plurality of blade channels, each of which is delimited by a respective first section and a respective second section of the surface of the hub. Furthermore, it follows that the diagonal impeller is rotatable about a rotation axis to which the diagonal impeller is arranged concentrically.
  • the prior art generally provides for the hub to have a completely and exclusively conical shape, in which the cross-section is round at every point along the longitudinal axis
  • the first and second sections of the surface of the hub in the area of the blade channel or the blade channels according to the invention ensure that the surface or the hub is leveled in the aerodynamically rear area of the blade channel or the blade channels.
  • the leveling or flattening in the aerodynamically rear area of the blade channel expands the flow cross-section of the blade channel, which leads to an improvement in efficiency, particularly in very limited installation space.
  • the design of the diagonal impeller according to the invention therefore contributes to increasing the power density.
  • the outside diameter of the diagonal impeller determined by the blades widens from the inflow side to the outflow side and preferably according to the conical shape of the hub. If the blades are covered by a cover plate, which will be explained below, the cover plate can also widen in terms of its diameter from the inflow side to the outflow side and preferably according to the conical shape of the hub.
  • the surface of the hub or the hub surface in the first section is curved rotationally symmetrically and/or convexly radially outward to a rotation axis of the diagonal impeller and thus corresponds to a partial surface of a conical or conical body and preferably to a partial surface of the conical basic shape of the hub.
  • all first sections of the surface of the hub correspond to partial surfaces of a common, ie single, imaginary cone or taper.
  • the first sections of the surface of the hub can also be partial surfaces of a common, i.e. single, imaginary sphere or hemisphere or an ellipsoid.
  • all second sections can each correspond to partial surfaces of a side surface of an imaginary pyramid or an imaginary pyramid-shaped body. It follows that such a pyramid or such a pyramid-shaped body has, in addition to its base, a number of side surfaces corresponding to the number of second sections.
  • the hub does not have to be completely or purely conical, but the shape of the hub can correspond to a hybrid of a cone and a pyramid, in which the first sections form the conical part of the hub and the second sections form the pyramidal part of the hub.
  • first section of the surface and the second section of the surface merge into one another continuously and/or rounded and/or via a continuous, i.e. jump-free, transition area.
  • a continuous, i.e. jump-free, transition area Such a corresponding transition results in less flow separation and turbulence, so that correspondingly less noise is generated.
  • the first section of the surface is preferably visible from an inflow-side plan view of the hub at least in sections and in particular completely without overlap, i.e., and is in particular not overlapped by the blades of the respective associated blade pair.
  • the second portion of the surface can be covered at least in sections by a blade, ie a blade of the associated blade pair, from an inflow-side plan view of the hub.
  • the surface of the hub has a third section after the second section in the flow direction, which is arranged on the outflow side of the blade channel, i.e. after the blade channel or outside the blade channel.
  • the second section of the surface and the third section of the surface merge into one another continuously and/or rounded and/or via a continuous, i.e. again jump-free, transition region.
  • all second sections of the surface can merge into a common, i.e. single, third section, which is preferably an outer surface of an imaginary cylinder. It follows that the outer surface of the cylinder or the third section of the surface of the hub runs completely around the axis of rotation, preferably in the circumferential direction, and further preferably concentrically.
  • the diagonal impeller can have a cover plate which partially covers the blades, ie in particular all the blades of the plurality of blades on the inflow side in a radially outer region and in particular defines an inflow opening radially inside.
  • the blade channel or channels are thereby preferably limited radially outward by the cover plate.
  • the design according to the invention enables smaller angle differences between the cover plate and the hub, which also has a positive effect on noise behavior and efficiency.
  • the blades, ie the blades of the blade pair and in particular all blades of the plurality of blades each have an inflow-side base point and an outflow-side base point, at which the blades each adjoin the hub, merge into the hub or are connected to it.
  • a boundary line between the first section and the second section of the surface runs in particular in a straight line from an inflow-side base point of a first blade of the blade pair or of a respective blade pair to an outflow-side base point of a second blade of the blade pair or of the respective blade pair.
  • the first portion of the surface preferably extends from the first blade of the blade pair to the boundary line and the second portion of the surface from the boundary line to the second blade of the blade pair.
  • the boundary line between the second section or sections and the third section forms a tangent to the outflow-side base points of the blades and connects or tangentially connects them to one another.
  • the boundary line between two outflow-side base points of two blades arranged directly next to one another can be curved in particular in the direction of flow and have a kink at each of the outflow-side base points.
  • the diagonal impeller can be designed in several parts, it is preferably provided that it is designed in one piece, so that the hub, Blades and, if present, the cover plate are firmly connected to one another. Furthermore, the diagonal impeller is preferably manufactured in an injection molding process using a tool with one-piece slides.
  • FIG. 1 inlet side perspective view of a diagonal impeller
  • Fig. 4a, b inlet side plan view of the diagonal impeller
  • Fig. 5 Inflow side plan view of the diagonal impeller with cross-sections of schematic basic bodies.
  • Figure 1 shows a diagonal impeller 1 in perspective, with the diagonal impeller being viewed from the inflow side A.
  • the diagonal impeller 1 has a hub 10 from which blades 20, and in this case five blades 20, extend outwards in the radial direction R. Furthermore, the diagonal impeller 1, which is completely formed in one piece, has a cover disk 30 which surrounds the rotation axis X in the circumferential direction. device II completely rotates and is connected to the blades 20 in a radially outer region thereof, so that an inflow opening 3 remains free radially inside.
  • FIG. 4b shows a section with exactly one blade pair 23 of the intake-side top view of the diagonal impeller 1 according to Figure 4a.
  • Each of the blade pairs 23 has a first blade 21 and a second blade 22, which define a blade channel 2 between them, through which a flow S shown as an example in Figure 2 can flow from the inflow side A to the outflow side B or is conveyed by the rotation of the diagonal impeller 1 about the axis of rotation X.
  • the blade channels 2 are each delimited radially on the inside by the hub 10 or the surface of the hub 10. According to the embodiment variant shown, the blade channels 2 are delimited radially on the outside by the cover disk 30.
  • the surface of the hub 10 delimiting the blade channel 2 has a first section 11 and a subsequent second section 12 in the flow direction, wherein the surface is curved in the first section 11 or has a curvature in the radial direction R and is flat in the second section 12.
  • the two sections 11, 12 and the transition area 14 between them can be seen particularly advantageously in the detailed representation of Figure 4b. This means that the flow cross section, ie the cross section of the Flow channel 2 in its area adjacent to the second section 12 is increased, particularly compared to its area adjacent to the first section 11, which leads to an improvement in efficiency.
  • transition region 14 between the first and second sections 11, 12 of the surface of the hub 10 is rounded, resulting in a relatively wide transition region 14 which, however, runs along a boundary line or covers or replaces it.
  • the hub 10 in addition to the essentially conical section, i.e. section which widens in the radial direction R and in which the first and second sections 11, 12 are also located, has a cylindrical section which determines a third section 13 of the surface of the hub 10.
  • transition region 14 from the first section 11 to the second section 12 does not run from the outflow-side base point 25 to the outflow-side base point 25, but - as can be seen in Figure 4a for all five transition regions 14 - from an inflow-side base point 24 of a first blade 21 of a blade pair 23 of two immediately adjacent blades 20 to an outflow-side base point 25 of a second blade 22 of the blade pair 23 of two immediately adjacent blades 20.
  • the transition region 14 between the first section 11 and the second section 12 runs in a straight line between these base points 24, 25 in order to optimize the flow.
  • Figure 4b corresponds to an enlarged detailed view of the diagonal impeller 1 according to Figure 4a, wherein in particular a pair of blades 23 formed from two immediately adjacent blades 20 and the blade channel 2 determined by the pair of blades 23 are shown.
  • This also makes the curved first section 11 of the surface of the hub 10, the flat or level second section 12 of the surface of the hub 10 and the transition region 14 between the first section 11 and the second section 12 particularly clearly visible.
  • the inflow side plan view in Figure 5 corresponds to the inflow side plan view according to Figure 4a, whereby for a clearer representation of the resulting from the first sections 11 and the second sections 12
  • imaginary cutting lines 16, 18 and base surfaces 17, 19 are drawn.
  • the first sections 11 correspond in this case to partial surfaces of a single imaginary cone, which also determines the conical basic shape of the hub 10.
  • the cutting lines 16 running in the first sections 11 form corresponding partial circles or parts of a common, i.e. single, circle 17.
  • the second sections 12 each correspond to partial surfaces of a side surface of a single imaginary and in this case five-sided pyramid, which determines the angular partial shape of the hub 10 or the angular part of the shape of the hub 10.
  • the cutting lines 18 running in the second sections 12 form corresponding lines as parts of a side surface of a common, i.e. single, pentagon 19, i.e. a regular pentagon 19.
  • the blades 20 of the diagonal impeller 1 are preferably evenly distributed and curved in the circumferential direction U around the axis of rotation.
  • the curvature of the blades 20 results in the second section 12 from the inflow side plan view of the hub 10, i.e. as shown in Figures 4a, 4b and Figure 5, being partially covered by one of the blades 20 of the blade pair 23 and the first section 11 of the surface being free of overlap.
  • the invention is not limited in its implementation to the preferred embodiments given above. Rather, a number of variants are conceivable which make use of the solution presented even in fundamentally different embodiments.

Landscapes

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

Abstract

L'invention concerne une roue diagonale (1) ayant un moyeu conique (10) qui s'étend d'un côté de débit entrant (A) à un côté de débit sortant (B) dans la direction radiale (R), une pluralité d'aubes (20) s'étendant radialement vers l'extérieur à partir du moyeu (10), chaque paire d'aubes (23), qui consiste en deux aubes (21, 22) directement adjacentes de la pluralité d'aubes (20), définissant, entre ladite paire, un canal d'aube (2) qui peut être traversé par un écoulement depuis le côté de débit entrant (A) vers le côté de débit sortant (B), le canal d'aube (2) étant délimité radialement vers l'intérieur par une surface du moyeu (10) qui s'étend entre les deux aubes (21, 22), la surface du moyeu (10) qui délimite le canal d'aube (2) ayant, dans la direction d'écoulement, une première portion (11) et une deuxième portion (12) suivante, la surface dans la première portion (11) étant incurvée et la surface dans la deuxième portion (12) étant plate.
PCT/EP2023/081400 2022-11-25 2023-11-10 Roue diagonale à face de moyeu variable Ceased WO2024110213A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022131248.8A DE102022131248B4 (de) 2022-11-25 2022-11-25 Diagonallaufrad mit variierender Nabenfläche
DE102022131248.8 2022-11-25

Publications (1)

Publication Number Publication Date
WO2024110213A1 true WO2024110213A1 (fr) 2024-05-30

Family

ID=88779064

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/081400 Ceased WO2024110213A1 (fr) 2022-11-25 2023-11-10 Roue diagonale à face de moyeu variable

Country Status (2)

Country Link
DE (1) DE102022131248B4 (fr)
WO (1) WO2024110213A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10005857A1 (de) * 1999-02-10 2000-08-31 Ecia Equip Composants Ind Auto Flügelrad, insbesondere für Lüftersatz
DE202010013785U1 (de) 2009-10-03 2011-02-17 Ebm-Papst St. Georgen Gmbh & Co. Kg Diagonalventilator
US20120325442A1 (en) * 2007-03-14 2012-12-27 Mitsubishi Electric Corporation Air conditioner
DE202018106513U1 (de) * 2018-11-16 2018-11-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonalventilator mit optimiertem Diagonallaufrad
WO2020099027A1 (fr) 2018-11-16 2020-05-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilateur diagonal présentant une réduction de rotation au niveau du rotor diagonal

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202004010088U1 (de) * 2004-06-25 2004-09-09 Ebm-Papst Mulfingen Gmbh & Co. Kg Laufrad, insbesondere für einen Axialventilator
PT2218917E (pt) * 2009-02-12 2013-04-11 Ebm Papst Mulfingen Gmbh & Co Compostos heterocíclicos condensados úteis como moduladores de quinase
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
DE102017114679A1 (de) * 2017-06-30 2019-01-03 Ebm-Papst Mulfingen Gmbh & Co. Kg Gebläserad
DE102018128821A1 (de) * 2018-11-16 2020-05-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonalventilator mit optimiertem Diagonallaufrad
DE102020104985A1 (de) * 2020-02-26 2021-08-26 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilatorrad eines Axial- oder Diagonalventilators mit Wuchtring
DE102020114389A1 (de) * 2020-05-28 2021-12-02 Ebm-Papst Mulfingen Gmbh & Co. Kg Gebläserad mit ener nahtlosen Anbindung der Laufradschaufeln an einen Scheibenkörper

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10005857A1 (de) * 1999-02-10 2000-08-31 Ecia Equip Composants Ind Auto Flügelrad, insbesondere für Lüftersatz
US20120325442A1 (en) * 2007-03-14 2012-12-27 Mitsubishi Electric Corporation Air conditioner
DE202010013785U1 (de) 2009-10-03 2011-02-17 Ebm-Papst St. Georgen Gmbh & Co. Kg Diagonalventilator
DE202018106513U1 (de) * 2018-11-16 2018-11-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonalventilator mit optimiertem Diagonallaufrad
WO2020099027A1 (fr) 2018-11-16 2020-05-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilateur diagonal présentant une réduction de rotation au niveau du rotor diagonal

Also Published As

Publication number Publication date
DE102022131248B4 (de) 2025-07-24
DE102022131248A1 (de) 2024-05-29

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