EP3702620B1 - Ventilateur axial pourvu d'aubes de roue de ventilateur réduisant le bruit et pourvues de trous - Google Patents

Ventilateur axial pourvu d'aubes de roue de ventilateur réduisant le bruit et pourvues de trous Download PDF

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Publication number
EP3702620B1
EP3702620B1 EP20155642.0A EP20155642A EP3702620B1 EP 3702620 B1 EP3702620 B1 EP 3702620B1 EP 20155642 A EP20155642 A EP 20155642A EP 3702620 B1 EP3702620 B1 EP 3702620B1
Authority
EP
European Patent Office
Prior art keywords
fan wheel
boreholes
blade tip
along
axial
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
EP20155642.0A
Other languages
German (de)
English (en)
Other versions
EP3702620A1 (fr
Inventor
Roland Keber
Tobias SIEGER
Wolfgang Laufer
Jürgen Herr
Arnold Schulde
Georg Eimer
Martin Müller
Dominik Haas
Simon HOPPE
Julien GRILLIAT
Johannes DANNECKER
Clemens GÜNTER
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 St Georgen GmbH and Co KG
Original Assignee
Ebm Papst St Georgen 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 St Georgen GmbH and Co KG filed Critical Ebm Papst St Georgen GmbH and Co KG
Priority to EP21215518.8A priority Critical patent/EP3988797B1/fr
Publication of EP3702620A1 publication Critical patent/EP3702620A1/fr
Application granted granted Critical
Publication of EP3702620B1 publication Critical patent/EP3702620B1/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
    • F04D29/66—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F04D19/005—Axial flow fans reversible fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • 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
    • F04D29/38—Blades
    • F04D29/388—Blades characterised by construction
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • 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
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • 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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • F05D2240/307—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 tip of a rotor blade
    • 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
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F05D2260/962—Preventing, counteracting or reducing vibration or noise by means of "anti-noise"

Definitions

  • the invention relates to an axial fan with a housing and a fan wheel arranged in the housing for generating an axial air flow through the housing.
  • the object of the invention is to improve the noise behavior of an axial fan.
  • an axial fan with a housing and a fan wheel arranged in the housing is proposed for generating an axial air flow through the housing.
  • the fan wheel has a plurality of fan wheel blades which extend radially outwards from a hub to the respective blade tip and which run at a distance from an inner wall of the housing via a head gap.
  • the blade tip is the extension of the fan wheel blades along the inner wall of the housing, which surrounds the fan wheel in particular as a housing ring.
  • the fan wheel blades have bores along the respective blade tip.
  • the holes along the respective blade tip interact directly with the tip gap vortex and reduce the noise emissions of the fan wheel during operation.
  • the shape and propagation of the flow vortex along the blade tips of the fan wheel blades is favorably influenced.
  • reductions in noise development were found in measurements of over 20% can be achieved.
  • the bores are particularly advantageous in axial fans in which the fan wheel blades have a very shallow angle of attack relative to the axial plane running perpendicular to the direction of flow, which is in particular in the range of 5-25°, preferably 10-20°.
  • the bores are formed on both axial sides of the fan wheel blades or as through-holes through the fan wheel blades.
  • the bores are provided for each fan wheel blade along the respective blade tip.
  • the number of holes is at least two, but in particular at least three, preferably at least five, more preferably at least seven.
  • the holes run along a line parallel to the blade tip. Their arrangement is thus defined by the course of the blade tip along the head gap in relation to the inner wall of the housing.
  • the bores with a circular cross-section has proven to be particularly favorable.
  • the size of the holes is determined by their diameter.
  • the bores have a maximum diameter DBmax, which corresponds to 0.7-1.5%, preferably 1%, of a maximum fan wheel diameter of the fan wheel.
  • a special arrangement of the holes in relation to each other also promotes noise reduction.
  • An embodiment variant is advantageous in which the bores are at a distance A from one another along the respective blade tip, which corresponds to twice the maximum diameter DBmax of the bores. The distance A is measured at the center of the respective hole. Based on the maximum fan wheel diameter D of the fan wheel, the distance A between the bores along the respective blade tip is advantageous if it corresponds to 2% of the maximum fan wheel diameter D.
  • the bores are spaced somewhat radially inward from the respective blade tip of the respective fan wheel blade but are nevertheless adjacent, so that the radially outer blade tip of the respective fan wheel blade runs continuously and uninterrupted.
  • the bores are preferably offset radially inward from the blade tip by 1.5 times the bore diameter.
  • measurements are always taken in the center of the bores.
  • the length LS with which the bores are spaced apart from the respective blade tip corresponds to preferably 1.5% of the maximum fan wheel diameter D of the fan wheel.
  • all bores of the fan wheel are each identical in terms of shape and size.
  • the bores are arranged over an extension along the blade tip of the respective fan wheel blade, which corresponds to 10-40% of a maximum extension of the blade tip along the head gap. This means that there is a predominant section along the blade tip in which no bores are provided, but in which a minimum quantity and a minimum extent must not be undershot. Furthermore, it is favorable that the bores are in particular in a region of the blade tip to be arranged, which is adjacent to the respective blade leading edge and / or respective blade trailing edge.
  • the axial fan provides that each of the fan wheel blades along the blade tip has a middle section which adjoins a radial center line of the fan wheel blades on both sides and is free of bores.
  • the bores are thus provided in an area of the front edge and rear edge of the fan wheel blades.
  • the middle section determines 20-90%, more preferably 40-80% of the maximum extent of the respective fan blade in the circumferential direction.
  • the bores are additionally provided along the front edge and/or the rear edge of the fan wheel blades.
  • the distances from one another or from the front edge and/or a rear edge preferably correspond to those of the bores along the blade tip or from the blade tip.
  • an embodiment is favorable in which, in the case of the axial fan, the respective number of bores along the front edge and/or the rear edge of the fan wheel blades is less than or equal to the number of bores along the blade tip. This means that the number of holes on the leading edge and on the trailing edge is always no greater than the number of holes on the blade tip.
  • the axial fan is further characterized in that the fan wheel is designed to be reversible and its generated during operation Flow direction depends on its direction of rotation. Then the bores are preferably provided both on the front edge and the rear edge as well as on both axial sides of the respective fan wheel blades.
  • a first embodiment variant of the axial fan 1 is shown.
  • This comprises a ring-shaped, closed housing 2 in which the reversible fan wheel 3 is arranged for generating the axial air flow, the direction of flow of which depends on the direction of rotation of the fan wheel 4 .
  • the fan wheel 3 has the hub 5 with a plurality of ventilation openings 25 arranged in a circle, in which the drive motor is accommodated, which is electrically connected via the connections 14 is supplied.
  • the drive motor is held by the holder 20, which is connected to the housing 2 via webs 11 distributed in the circumferential direction.
  • the webs 11 run in a straight line, but are inclined relative to a radial plane.
  • the fan wheel blades 4 extend radially outward from the hub 5 to their respective blade tip 8 , which forms the blade edge adjoining the inner wall of the housing 2 .
  • the head gap 12 is provided between the blade tips 8 and the inner wall of the housing 2 so that the fan wheel 3 can rotate relative to the housing 2 .
  • the fan wheel blades 4 are each shaped identically. Adjacent to the blade tip 8 , viewed in the circumferential direction, they each have a radially constricted section 9 on both sides, in which the blade edge still points radially outward, but is at a distance from the inner wall of the housing 2 .
  • the blade edge then transitions into the front edge 17 and rear edge 18 , which each point in the circumferential direction, but are designed to be drawn in in the circumferential direction compared to the radially outermost section of the fan wheel blade 4 .
  • An axial step 24 is formed on each of the fan wheel blades 4 along their central axis, viewed in the circumferential direction, which increases in size viewed radially inward and tapers off towards the blade tip 8, so that the impeller blade 4 runs steplessly in the area of the blade tip 8.
  • a plurality of bores 7 with a circular cross-section are provided on each of the fan wheel blades 4 along the respective blade tip 8 on both axial sides.
  • the bores 7 are formed on both axial sides at the respective identical position and thus have the respective identical central axis.
  • the bores 7 are designed as through bores.
  • a total of 16 bores 7 are provided per fan blade 4 , of which six bores 7 are located in each area with bores 7 along the blade tip 8 along the head gap 12 and two bores 7 in each case in the drawn-in section 9 .
  • each of the fan wheel blades 4 comprises a central section 15 along the blade tip 8 which adjoins a radial center line of the fan wheel blades 4 on both sides and is free of bores 7 .
  • the middle section 15 without holes 7 determined in both versions according to figures 1 and 5 No bores 7 are provided in the comparatively larger area, ie over a larger extent of the respective fan wheel blade 4, since these are essentially located in the peripheral edge sections.
  • the fan wheel blades 4 have a very small angle of attack of less than 25° with respect to the axial plane extending through the housing 2, which is good in figure 3 can be seen. With such small angles of attack, the bores are 7 particularly effective.
  • the size, shape and arrangement of the holes 7 influences the noise-reducing effect significantly.
  • advantageous dimensions which are identical for the embodiment of Figures 1-4 are applicable.
  • the bores 7 have a maximum diameter DBmax, which corresponds to 1% of the maximum fan wheel diameter D of the fan wheel 4, measured in each case in the center of the bores 7.
  • the distance A of the bores 7 to one another along the respective blade tip 8 corresponds to twice the maximum diameter DBmax and 2 % of the maximum impeller diameter D of the impeller 4.
  • the bores 7 are spaced apart from the blade tip 8 over the length LS, which makes up 1.5% of the impeller diameter D and 1.5 times the maximum diameter DBmax.
  • the radially outer blade tip 8 of the respective fan blade 4 runs continuously and without interruption.
  • the bores 7 are distributed along the blade tip 8 over a length which corresponds to 10% of the blade tip length L, along which the tip gap 12 is formed. In the execution according to Figures 1 - 4 it is 20%.

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

Claims (13)

  1. Ventilateur axial (1) doté d'un boîtier (2) et d'une roue de ventilateur (3) disposée dans le boîtier (2) pour générer un écoulement d'air axial à travers le boîtier (2), dans lequel la roue de ventilateur (3) présente plusieurs pales de roue de ventilateur (4) s'étendant depuis un moyeu (5) vers l'extérieur dans le sens radial jusqu'à la pointe de pale (8) respective, lesquelles pales de roue de ventilateur sont espacées d'une paroi intérieure du boîtier (2) par un entrefer (12), dans lequel les pales de roue de ventilateur (4) présentent des alésages (7) le long de la pointe de pale (8) respective dans la zone d'un bord avant (17) et d'un bord arrière (18) des pales de roue de ventilateur (4), dans lequel chacune des pales de roue de ventilateur (4) présente le long de la pointe de pale (8) respectivement une section centrale (15) adjacente des deux côtés à une ligne centrale radiale des pales de roue de ventilateur (4) et qui est exempte d'alésages (7), dans lequel la section centrale détermine 20 à 90 % d'une extension de la pale de roue de ventilateur (4) respective dans le sens circonférentiel, et dans lequel les alésages (7) sont formés sur les deux côtés axiaux des pales de roue de ventilateur (4) ou sous forme d'alésages traversants à travers les pales de roue de ventilateur (4).
  2. Ventilateur axial selon la revendication 1, caractérisé en ce que les pales de roue de ventilateur (4) présentent un petit angle d'attaque par rapport à un plan axial compris dans la plage de 5 à 25°, en particulier de 10 à 20°.
  3. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que le nombre d'alésages (7) par pale de roue de ventilateur (4) le long de la pointe de pale (8) respective est d'au moins deux, en particulier d'au moins trois, en particulier d'au moins cinq, et dans lequel les alésages (7) sont disposés le long d'une ligne parallèle à la pointe de pale (8).
  4. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) présentent une section circulaire.
  5. Ventilateur axial selon la revendication précédente, caractérisé en ce que les alésages (7) présentent un diamètre maximal DBmax, qui correspond à 1 % d'un diamètre de roue de ventilateur maximal D de la roue de ventilateur (3).
  6. Ventilateur axial selon la revendication précédente, caractérisé en ce que les alésages (7) présentent une distance A entre eux le long de la pointe de pale (8) respective qui correspond à deux fois le diamètre maximal DBmax, dans lequel la distance est mesurée respectivement au centre de chaque alésage (7).
  7. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) présentent une distance A entre eux le long de la pointe de pale (8) respective qui correspond à 2 % d'un diamètre de roue de ventilateur maximal D de la roue de ventilateur (3).
  8. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) présentent un diamètre maximal DBmax et sont espacés de la pointe de pale (8) respective sur une longueur LS, de sorte que l'on a : DBmax ≤ LS ≤ 2,5 x DBmax, en particulier LS=1,5 x DBmax.
  9. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) sont espacés de la pointe de pale (8) respective d'une longueur LS qui correspond à 1,5 % d'un diamètre de roue de ventilateur maximal D de la roue de ventilateur.
  10. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) sont prévus sur une extension le long de la pointe de pale (8) de la pale de roue de ventilateur (4) respective qui correspond à 10 à 40 % d'une extension maximale de la pointe de pale (8) le long de l'entrefer.
  11. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que les alésages (7) sont en outre prévus le long du bord avant (17) et/ou du bord arrière (18) des pales de roue de ventilateur (4).
  12. Ventilateur axial selon la revendication précédente, caractérisé en ce qu'un nombre respectif d'alésages supplémentaires (7) le long du bord avant (17) et/ou du bord arrière (18) des pales de roue de ventilateur est inférieur ou égal à un nombre d'alésages (7) le long de la pointe de pale (8).
  13. Ventilateur axial selon l'une des revendications précédentes, caractérisé en ce que la roue de ventilateur (3) est conçue pour être réversible et que son sens d'écoulement généré pendant le fonctionnement dépend de son sens de rotation.
EP20155642.0A 2019-02-28 2020-02-05 Ventilateur axial pourvu d'aubes de roue de ventilateur réduisant le bruit et pourvues de trous Active EP3702620B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21215518.8A EP3988797B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu de pales de roue d'aérateur réduisant le bruit et pourvues de trous

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019105190.8A DE102019105190A1 (de) 2019-02-28 2019-02-28 Axialventilator mit geräuschreduzierenden Lüfterradschaufeln

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP21215518.8A Division EP3988797B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu de pales de roue d'aérateur réduisant le bruit et pourvues de trous
EP21215518.8A Division-Into EP3988797B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu de pales de roue d'aérateur réduisant le bruit et pourvues de trous

Publications (2)

Publication Number Publication Date
EP3702620A1 EP3702620A1 (fr) 2020-09-02
EP3702620B1 true EP3702620B1 (fr) 2022-04-27

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EP20155642.0A Active EP3702620B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu d'aubes de roue de ventilateur réduisant le bruit et pourvues de trous
EP21215518.8A Active EP3988797B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu de pales de roue d'aérateur réduisant le bruit et pourvues de trous

Family Applications After (1)

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EP21215518.8A Active EP3988797B1 (fr) 2019-02-28 2020-02-05 Ventilateur axial pourvu de pales de roue d'aérateur réduisant le bruit et pourvues de trous

Country Status (6)

Country Link
US (1) US11391282B2 (fr)
EP (2) EP3702620B1 (fr)
KR (1) KR102320943B1 (fr)
CN (1) CN210050072U (fr)
DE (1) DE102019105190A1 (fr)
PL (2) PL3988797T3 (fr)

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USD972706S1 (en) * 2019-02-28 2022-12-13 Ebm-Papst St. Georgen Gmbh & Co. Kg Ventilating fan
DE102019105355B4 (de) * 2019-03-04 2024-04-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Lüfterrad eines Axialventilators
USD972707S1 (en) * 2019-04-29 2022-12-13 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilating fan
DE102021116749A1 (de) 2021-06-29 2022-12-29 Stiebel Eltron Gmbh & Co. Kg Dezentrales Lüftungsgerät und Strömungsgleichrichter
USD1028366S1 (en) * 2023-08-28 2024-05-21 Xu Wang Nail vacuum cleaner

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CN107489658A (zh) 2017-08-31 2017-12-19 中国航天空气动力技术研究院 基于叶片改型的电风扇降噪方法及改进的电风扇叶片结构
CN107313979B (zh) 2017-08-31 2019-04-30 广东美的制冷设备有限公司 轴流风轮及具有其的空调器
USD897520S1 (en) * 2017-12-13 2020-09-29 Ebm-Papst Mulfingen Gmbh & Co. Kg Fan
USD903085S1 (en) * 2017-12-13 2020-11-24 Ebm-Papst Mulfingen Gmbh & Co. Kg Fan
WO2020091150A1 (fr) * 2018-10-30 2020-05-07 주식회사 명성 Filet de sécurité pour ventilateur

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CN210050072U (zh) 2020-02-11
KR102320943B1 (ko) 2021-11-04
KR20200105627A (ko) 2020-09-08
EP3702620A1 (fr) 2020-09-02
US11391282B2 (en) 2022-07-19
PL3702620T3 (pl) 2022-08-16
EP3988797B1 (fr) 2022-11-23
US20200277962A1 (en) 2020-09-03
PL3988797T3 (pl) 2023-03-06
DE102019105190A1 (de) 2020-09-03
EP3988797A1 (fr) 2022-04-27

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