EP2363609A1 - Radial- oder Diagonal-Ventilatorrad - Google Patents

Radial- oder Diagonal-Ventilatorrad Download PDF

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Publication number
EP2363609A1
EP2363609A1 EP11153316A EP11153316A EP2363609A1 EP 2363609 A1 EP2363609 A1 EP 2363609A1 EP 11153316 A EP11153316 A EP 11153316A EP 11153316 A EP11153316 A EP 11153316A EP 2363609 A1 EP2363609 A1 EP 2363609A1
Authority
EP
European Patent Office
Prior art keywords
fan
rotationally symmetrical
fan wheel
wheel according
blade
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.)
Withdrawn
Application number
EP11153316A
Other languages
German (de)
English (en)
French (fr)
Inventor
Katrin Bohl
Marc Schneider
Jürgen Schöne
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
Priority to KR1020110016107A priority Critical patent/KR101764430B1/ko
Priority to US13/034,295 priority patent/US8932019B2/en
Priority to CN201110049513.8A priority patent/CN102168684B/zh
Priority to CA2732714A priority patent/CA2732714A1/en
Priority to JP2011042557A priority patent/JP5804348B2/ja
Publication of EP2363609A1 publication Critical patent/EP2363609A1/de
Withdrawn legal-status Critical Current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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S416/00—Fluid reaction surfaces, i.e. impellers
    • Y10S416/50—Vibration damping features

Definitions

  • the present invention relates according to the preamble of claim 1, a fan wheel in an embodiment as a radial or diagonal fan, consisting of a cover plate with an inlet opening, a bottom plate and a plurality of circumferentially disposed about the inlet opening and around a rotation axis arranged fan blades and with in the circumferential direction each formed between the adjacent fan blades blade channels that lead radially or diagonally outward from the region of the inlet opening and form outlet openings at the outside, the blade channels are designed so large with respect to their effective flow cross-section that in operation a turbulent flow with a Reynolds number clearly greater than 2300 is reached, and wherein the cover disk and / or the bottom disk have / have a non-rotationally symmetric geometry.
  • turbomachinery Such fan wheels are referred to as turbomachinery (turbo fan) because of the turbulent flow.
  • Characteristic here is the very high Reynolds number Re, which, with a value of at least 5000 (ie Re ⁇ 5000), is clearly larger by a factor> 2 than the well-known limit of about 2300 between laminar flow (Re ⁇ 2300) and turbulent flow (Re> 2300) is. In most cases, however, even Re ⁇ 10000 (factor> 4) and can be up to several 10000 (eg around 35000).
  • the turbulent flow in the blade channels achieves a high efficiency in the range above 0.6 and up to at least 0.8 (60-80%).
  • non-rotationally symmetrical means that any two different radial sections of the bottom plate and / or the cover plate are not congruent at different circumferential angles in two planes which include the axis of rotation and enclose a certain differential angle in the circumferential direction, but from each other differ.
  • a deviation could basically be present in the direction of the axis of rotation (axially) and / or in the radial direction (radially).
  • rotation of the body about certain angles about the axis of rotation does not imitate the object or its intersection on itself.
  • each fan wheel should have an obliquely stepped contour in the circumferential direction.
  • the step shape causes each fan blade on its suction side and its pressure side has different (measured axially) outlet widths, and indeed, depending on embodiment, the outlet width on the suction side be smaller or larger than the outlet width on the pressure side.
  • the EP 1 933 039 A1 describes a radial fan with ribs, recesses or incisions on the outside of the cover plate. This embodiment should lead to a noise reduction by a certain flow guidance.
  • EP 1 032 766 B1 describes a fan especially for a turbocharger.
  • this fan blades are formed by embossing on at least one of the two discs (bottom and / or cover disc). These imprints also create a non-rotationally symmetric geometry.
  • this publication is not concerned with influencing the flow, but has mainly manufacturing and stability-promoting aspects to the content.
  • each fan blade and / or each cover disc consists of two should consist of separate layers, which are connected in the manner of "corrugated cardboard" on wavy connecting webs. Although this results in a non-rotationally symmetrical course between the two layers, the surfaces of the cover plates which are responsible for the flow properties are in any case rotationally symmetrical.
  • the "corrugated board” mechanically reinforced cavity between the layers is not flowed through.
  • the present invention is based on the object to provide a fan wheel of the type described above, with the improved mechanical stability of the flow for optimization in terms of air performance, efficiency and noise performance is achieved.
  • a first aspect of the invention is according to claim 1 in that the respective non-rotationally symmetrical cover disc or bottom disc additionally seen in the axial or axis-parallel direction a continuous, punctiform course on the respective outer sides of the bottom and / or cover plate over the entire circumference (also over the regions of the blades).
  • the geometry deviation of two different, the axis of rotation containing sections of each non-rotationally symmetric disc (top or bottom disc) in the radial direction be arbitrary (in contrast to the invention in any case punctiform course in the axial direction). This means that radially either a punctiform or a jump-shaped course is possible.
  • an inventive fan wheel 1 to be driven in rotation about a rotation axis Z comprises a cover disk 2 with a preferably substantially central inlet opening 4 for air inlet, a bottom disk 6 opposite in the axial direction Z and a plurality of fan blades 8.
  • These fan blades 8 are located between the bottom disk 6 and the Cover disc 2 arranged or formed entirely or partially by a specific shaping of the bottom plate 6 and / or the cover plate 2 (see. Fig. 8 ), wherein the discs 2, 6 are then connected directly in these areas.
  • the fan blades 8 are arranged in a certain circumferential distribution about the rotation axis Z and the inlet opening 4 around. In the circumferential direction, in each case between two adjacent fan blades 8, blade channels 10 are formed, which lead radially or diagonally outwardly from the region of the inlet opening 4 and form outlet openings 11 on the outer region of the fan wheel 1.
  • the blade channels 10 are designed so large with respect to their effective flow cross-section that during operation a turbulent flow with a Reynolds number Re »2300 at high efficiency between 0.6 and 1.0 is achieved.
  • the inlet opening 4 has an effective suction mouth flow distance D s whose ratio to an effective flow distance D k of each blade channel is in any case less than 10, in particular even less than 3.
  • the mentioned flow widths are usually related to a circular shape, so that an idealized diameter is used as a basis, even if the actual flow cross sections deviate from the circular shape.
  • the cover disk 2 or the bottom disk 6 or each of the two disks 2, 6 it is now essential for the cover disk 2 or the bottom disk 6 or each of the two disks 2, 6 to have a non-rotationally symmetrical geometry for influencing the flow.
  • the cover plate 2 and the bottom plate 6 are not parallel to each other.
  • Non-rotational symmetry in the sense of the present invention is when the lying in the planes E1 and E2 cross-sectional areas of respective disc 2 and / or 6 differ - at different circumferential angles - from each other.
  • the geometry deviation of two different cuts containing the rotation axis Z in the radial direction (radius r in FIG Fig. 10 ) be arbitrary. This means that both punctiform and jump-like courses are possible here.
  • Fig. 1 In the execution according to Fig. 1 is the cover plate 2 in the region of the inlet opening 4 equipped with a wheel inlet 12, wherein the cover plate 2 is executed in the region of this wheel inlet 12 non-rotationally symmetrical in the direction of the axis of rotation Z.
  • the wheel inlet 12 extends web-like axially away from the cover plate 2 and has in the circumferential direction on a wavy contour with axial elevations and recesses lying therebetween.
  • the fan wheel 1 is designed in this case as a centrifugal fan.
  • the Cover disk 2 in the region of the inlet opening 2 and the Radeinlasses 12 also be formed non-rotationally symmetrical in the radial direction.
  • Fig. 2 it is a radial fan, in which case only the cover plate 2 is non-rotationally symmetrical in the direction of the axis of rotation Z.
  • the cover plate 2 is designed to be wavy in the circumferential direction, wherein in each case between two fan blades 8, a convex outwardly bulging portion is formed. These sections are continuous in the area of each fan blade 8 into each other.
  • Fig. 3 an embodiment is shown as a radial fan, in which only the bottom plate 6 is non-rotationally symmetrical in the axial direction Z executed. Specifically, it may be a similar design, as in the cover plate 2 according to Fig. 2 is provided.
  • FIG. 5 an embodiment of the fan wheel 1 is illustrated as a diagonal fan, wherein the cover plate 2 in the radial direction r is non-rotationally symmetrical, in this case not steadily, but jump-shaped. This is achieved by a non-continuous, but jumping over corners in radius course of an outer peripheral edge 14 of the cover plate 2.
  • the Fig. 6 shows an embodiment as a radial fan, wherein the cover plate 2 is designed in the radial direction r non-rotationally symmetrical, namely point-like. This means that the cover plate 2 here has a continuous circumferential course without corners or other cracks.
  • the Fig. 8 shows an embodiment as a radial fan, both discs, both the cover plate 2 and the bottom plate 6, are executed by a circumferentially wavy contour in the direction of the axis of rotation Z non-rotationally symmetrical.
  • the cover disk 2 and the bottom disk 6 are directly connected to one another in the outer circumferential region of the fan wheel 1 and thus together form at least a portion of the fan blades 8.
  • the fan blades 8 could be completely formed by the fact that the correspondingly shaped bottom and / or cover plates 6, 2 are connected directly to one another over the entire course of the blades 8.
  • the discs 2, 6 are connected to each other only in the outer peripheral region, wherein 10 conventional blade sections are formed as separate parts in the inner inlet region of the blade channels.
  • the non-rotationally symmetric design produces geometric structures which are periodically recurring in the circumferential direction.
  • FIG. 9 This is an embodiment in Fig. 9 illustrated. Again, this is a centrifugal fan with non-rotationally symmetrical cover plate 2. This has at a peripheral point 16 a leaps and bounds changing radius r, and the outer peripheral edge 14 of the cover plate 2 extends from the peripheral point 16 with a continuously changing radius over the circumference and ends after 360 ° again at the radius jump in the peripheral point 16. As a result, in this example, the peripheral edge 14 is spiraled.
  • the fan blades 8 may have any desired course. For example, they may be curved forward or backward with respect to the direction of rotation.
  • the invention is not limited to the illustrated and described embodiments, but also includes all the same in the context of the invention embodiments. It is expressly emphasized that the exemplary embodiments are not limited to all the features in combination, but each individual feature may also have an inventive meaning detached from all other features. Furthermore, the invention has not yet been defined in the respective independent claim Feature combination limited, but can also be defined by any other combination of certain features of all the individual features disclosed. This means that in principle virtually every individual feature of the respective independent claim can be omitted or replaced by at least one individual feature disclosed elsewhere in the application. In this respect, the claims are to be understood merely as a first formulation attempt for an invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP11153316A 2010-02-26 2011-02-04 Radial- oder Diagonal-Ventilatorrad Withdrawn EP2363609A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1020110016107A KR101764430B1 (ko) 2010-02-26 2011-02-23 레이디얼 또는 다이어고날 팬 임펠러
US13/034,295 US8932019B2 (en) 2010-02-26 2011-02-24 Radial or diagonal fan wheel
CN201110049513.8A CN102168684B (zh) 2010-02-26 2011-02-28 径流式或斜流式风扇叶轮
CA2732714A CA2732714A1 (en) 2010-02-26 2011-02-28 Radial or diagonal fan wheel
JP2011042557A JP5804348B2 (ja) 2010-02-26 2011-02-28 遠心式送風機または斜流送風機に用いられるインペラ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010009566A DE102010009566A1 (de) 2010-02-26 2010-02-26 Radial- oder Diagonal-Ventilatorrad

Publications (1)

Publication Number Publication Date
EP2363609A1 true EP2363609A1 (de) 2011-09-07

Family

ID=43806947

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11153316A Withdrawn EP2363609A1 (de) 2010-02-26 2011-02-04 Radial- oder Diagonal-Ventilatorrad

Country Status (7)

Country Link
US (1) US8932019B2 (enExample)
EP (1) EP2363609A1 (enExample)
JP (1) JP5804348B2 (enExample)
KR (1) KR101764430B1 (enExample)
CN (1) CN102168684B (enExample)
CA (1) CA2732714A1 (enExample)
DE (2) DE202010018509U1 (enExample)

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EP3048308A1 (en) * 2015-01-22 2016-07-27 LG Electronics Inc. Centrifugal fan

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DE102015101938A1 (de) 2015-02-11 2016-08-11 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilatorrad und Ventilator
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CN109654059B (zh) * 2018-12-29 2025-05-02 追觅创新科技(苏州)有限公司 叶轮和电机
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CN110836193B (zh) * 2019-12-19 2024-11-26 湖南联诚轨道装备有限公司 一种非对称式离心叶轮风机
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CN115342078B (zh) * 2022-10-20 2023-03-24 杭州顿力电器有限公司 一种带模块扩压结构的高效离心风机
WO2024191847A1 (en) * 2023-03-10 2024-09-19 Greenheck Fan Corporation High efficiency fan wheel
DE102023112165A1 (de) * 2023-05-09 2024-11-14 Ebm-Papst Mulfingen Gmbh & Co. Kg Kühlrad zur drehrichtungsunabhängigen Kühlung eines Elektromotors sowie Elektromotor mit einem solchen Kühlrad
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DE102023126038A1 (de) * 2023-09-26 2025-03-27 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüfterrad mit einer eine Welligkeit aufweisenden Begrenzungsfläche sowie Lüfter mit einem solchen Lüfterrad

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GB438036A (en) 1934-05-09 1935-11-11 Federated Engineers Ltd Improvements in blowers and the like
DE2940773C2 (de) 1979-10-08 1986-08-14 Punker GmbH, 2330 Eckernförde Hochleistungs-Radialventilator
DE3247453C1 (de) 1982-12-22 1983-12-15 Funken & Co GmbH, 5200 Siegburg Ventilatorlaufrad und Verfahren zu seiner Herstellung
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EP3048308A1 (en) * 2015-01-22 2016-07-27 LG Electronics Inc. Centrifugal fan
CN105822572A (zh) * 2015-01-22 2016-08-03 Lg电子株式会社 离心式风扇
US9989073B2 (en) 2015-01-22 2018-06-05 Lg Electronics Inc. Centrifugal fan

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JP2011179499A (ja) 2011-09-15
KR20110098649A (ko) 2011-09-01
KR101764430B1 (ko) 2017-08-02
CN102168684A (zh) 2011-08-31
CA2732714A1 (en) 2011-08-26
DE202010018509U1 (de) 2017-03-15
JP5804348B2 (ja) 2015-11-04
CN102168684B (zh) 2015-09-23
DE102010009566A9 (de) 2012-03-01
US8932019B2 (en) 2015-01-13
US20110211963A1 (en) 2011-09-01

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