EP3988797B1 - Axial fan with noise reducing fan impeller vanes having bores - Google Patents

Axial fan with noise reducing fan impeller vanes having bores Download PDF

Info

Publication number
EP3988797B1
EP3988797B1 EP21215518.8A EP21215518A EP3988797B1 EP 3988797 B1 EP3988797 B1 EP 3988797B1 EP 21215518 A EP21215518 A EP 21215518A EP 3988797 B1 EP3988797 B1 EP 3988797B1
Authority
EP
European Patent Office
Prior art keywords
fan
fan wheel
boreholes
blade tip
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
EP21215518.8A
Other languages
German (de)
French (fr)
Other versions
EP3988797A1 (en
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
Publication of EP3988797A1 publication Critical patent/EP3988797A1/en
Application granted granted Critical
Publication of EP3988797B1 publication Critical patent/EP3988797B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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.
  • shape and propagation of the flow vortex along the blade tips of the fan wheel blades is favorably influenced.
  • reductions in noise development of more than 20% could be achieved in measurements.
  • the bores are particularly advantageous in axial fans in which the fan impeller blades have a very shallow angle of attack with respect to the axial plane perpendicular to the direction of flow, which is in particular in the range of 5-25°, preferably 10-20°.
  • a development of the axial fan is characterized in that the bores are formed on both axial sides of the fan wheel blades.
  • the bores are designed as through bores through the fan wheel blades.
  • the bores are provided for each fan wheel blade along the respective blade tip.
  • the number of holes is 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.
  • 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.
  • An embodiment that is advantageous in terms of noise generation is characterized in that the bores have a maximum diameter DBmax and are spaced apart from the respective blade tip over a radial length LS, so that: DBmax ⁇ LS ⁇ 2.5 ⁇ DBmax.
  • 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 by 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 to arrange the bores in particular in a region of the blade tip which adjoins the respective front edge and/or the respective rear edge of the blade.
  • 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 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 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 direction of flow generated during operation depends on its direction of rotation. Then the holes are preferably both on the leading edge and the trailing edge and provided on both axial sides of the respective fan 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 supplied via the connections 14 .
  • 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 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 merges 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. Provision is preferably made for the bores 7 to be in the form of through bores.
  • eight bores 7 are provided on the two end sections pointing towards the front edge 17 and the rear edge 18 along the blade tip 8, i.e. a total of 16 bores 7 per fan wheel 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 holes 7 in the retracted section 9 are located.
  • 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 7 are 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 holes 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 fan wheel diameter D of the Fan wheel 4.
  • the holes 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%.

Description

Die Erfindung betrifft einen Axialventilator mit einem Gehäuse und einem in dem Gehäuse angeordneten Lüfterrad zur Erzeugung eines Axialluftstromes durch das Gehäuse.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.

Bei Axialventilatoren mit ringförmigen, das Lüfterrad umschließenden Gehäusen entstehen am Kopfspalt zwischen den Lüfterradschaufeln und der Gehäuseinnenwand Kopfspaltwirbel, die in Praxis zu einer erheblichen Geräuschentwicklung führen. Zu deren Reduzierung gibt es im Stand der Technik bereits mehrere Ansätze, die jedoch nicht für jeden Einsatz geeignet sind. Beispielsweise kann der Durchmesser des Axialventilators vergrößert werden. Dies ist jedoch kontraproduktiv hinsichtlich seines Wirkungsgrads und Windlastverhaltens. Alternativ gibt es die Möglichkeit, die Zuströmung oder Abströmung zu beeinflussen, jedoch sind hierfür zusätzliche Bauteile und meist ein erhöhter Bauraumbedarf nötig. Druckschriftlicher Stand der Technik ist in den Dokumenten CN 107 313 979 A , JP 2005 240749 A , CN 107 489 658 A und JP H11 201090 A offenbart.In the case of axial fans with ring-shaped housings surrounding the fan wheel, head gap vortices occur at the head gap between the fan wheel blades and the inner wall of the housing, which in practice lead to considerable noise development. To reduce them, there is in the state of Technology already has several approaches, but they are not suitable for every application. For example, the diameter of the axial fan can be increased. However, this is counterproductive with regard to its efficiency and wind load behavior. Alternatively, there is the possibility of influencing the inflow or outflow, but this requires additional components and usually more space. Printed state of the art is in the documents CN 107 313 979 A , JP 2005 240749A , CN 107 489 658 A and JP H11 201090 A disclosed.

Der Erfindung liegt die Aufgabe zugrunde, das Geräuschverhalten eines Axialventilators zu verbessern.The object of the invention is to improve the noise behavior of an axial fan.

Diese Aufgabe wird durch die Merkmalskombination gemäß Patentanspruch 1 gelöst.This object is achieved by the combination of features according to claim 1.

Erfindungsgemäß wird ein Axialventilator mit einem Gehäuse und einem in dem Gehäuse angeordneten Lüfterrad zur Erzeugung eines Axialluftstromes durch das Gehäuse vorgeschlagen. Das Lüfterrad weist mehrere sich von einer Nabe nach radial außen bis zur jeweiligen Schaufelspitze erstreckende Lüfterradschaufeln auf, welche über einen Kopfspalt beabstandet zu einer Innenwand des Gehäuses verlaufen. Die Schaufelspitze ist die Erstreckung der Lüfterradschaufeln entlang der Innenwand des Gehäuses, das insbesondere als Gehäusering das Lüfterrad umgibt. Die Lüfterradschaufeln weisen entlang der jeweiligen Schaufelspitze Bohrungen auf.According to the invention, 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.

Die Bohrungen entlang der jeweiligen Schaufelspitze interagieren unmittelbar mit dem Kopfspaltwirbel und reduzieren die Geräuschemission des Lüfterrads im Betrieb. Insbesondere wird die Form und Ausbreitung des Strömungswirbels entlang der Schaufelspitzen der Lüfterradschaufeln günstig beeinflusst. Bei Axialventilatoren, die sich ausschließlich durch die Laufradschaufeln mit und ohne entlang der Schaufelspitze vorgesehene Bohrungen unterschieden, konnten bei Messungen Reduzierungen der Geräuschentwicklung von über 20% erreicht werden.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. In particular, the shape and propagation of the flow vortex along the blade tips of the fan wheel blades is favorably influenced. In the case of axial fans, which only differ in the impeller blades with and without bores provided along the blade tips, reductions in noise development of more than 20% could be achieved in measurements.

Besonders vorteilhaft wirken die Bohrungen bei Axialventilatoren, bei denen die Lüfterradschaufeln einen sehr flachen Anstellwinkel gegenüber der senkrecht zur Strömungsrichtung verlaufenden Axialebene aufweisen, der insbesondere im Bereich von 5-25°, vorzugsweise 10-20° liegt.The bores are particularly advantageous in axial fans in which the fan impeller blades have a very shallow angle of attack with respect to the axial plane perpendicular to the direction of flow, which is in particular in the range of 5-25°, preferably 10-20°.

Eine Weiterbildung des Axialventilators ist dadurch gekennzeichnet, dass die Bohrungen auf beiden axialen Seiten der Lüfterradschaufeln ausgebildet sind. In einer bevorzugten Ausführung sind die Bohrungen als Durchgangsbohrungen durch die Lüfterradschaufeln ausgebildet.A development of the axial fan is characterized in that the bores are formed on both axial sides of the fan wheel blades. In a preferred embodiment, the bores are designed as through bores through the fan wheel blades.

Erfindungsgemäß werden mehrere der Bohrungen je Lüfterradschaufel entlang der jeweiligen Schaufelspitze vorgesehen. Die Anzahl der Bohrungen beträgt vorzugsweise mindestens fünf, weiter bevorzugt mindestens sieben. Die Bohrungen verlaufen dabei entlang einer Linie parallel zur Schaufelspitze. Ihre Anordnung ist somit über den Verlauf der Schaufelspitze entlang des Kopfspalts gegenüber der Innenwand des Gehäuses festgelegt.According to the invention, several of the bores are provided for each fan wheel blade along the respective blade tip. The number of holes is 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.

Als besonders günstig hat sich eine Ausführung der Bohrungen mit einem kreisförmigen Querschnitt erwiesen. Die Größe der Bohrungen wird über ihren Durchmesser bestimmt. In einer vorteilhaften Ausführung des Axialventilators weisen die Bohrungen einen maximalen Durchmesser DBmax auf, der 0,7-1,5%, vorzugsweise 1% eines maximalen Lüfterraddurchmessers des Lüfterrads entspricht.An embodiment of the bores with a circular cross-section has proven to be particularly favorable. The size of the holes is determined by their diameter. In an advantageous embodiment of the axial fan, 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.

Eine spezielle Anordnung der Bohrungen zueinander begünstigt die Geräuschreduzierung ebenfalls. Günstig ist eine Ausführungsvariante, bei der die Bohrungen zueinander einen Abstand A entlang der jeweiligen Schaufelspitze aufweisen, der dem doppelten maximalen Durchmesser DBmax der Bohrungen entspricht. Der Abstand A wird dabei jeweils am Mittelpunkt der jeweiligen Bohrung gemessen. Bezogen auf den maximalen Lüfterraddurchmesser D des Lüfterrads ist der Abstand A der Bohrungen entlang der jeweiligen Schaufelspitze zueinander dann vorteilhaft, wenn er 2% des maximalen Lüfterraddurchmessers D entspricht.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. In relation to 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.

Ferner ist vorteilhaft, dass die Bohrungen von der jeweiligen Schaufelspitze der jeweiligen Lüfterradschaufel nach radial innen etwas beabstandet gleichwohl angrenzend sind, so dass die radial außen liegende Schaufelspitze der jeweiligen Lüfterradschaufel durchgängig und ununterbrochen verläuft. Eine bezüglich der Geräuscherzeugung vorteilhafte Ausführung ist dadurch gekennzeichnet, dass die Bohrungen einen maximalen Durchmesser DBmax aufweisen und von der jeweiligen Schaufelspitze über eine radiale Länge LS beabstandet sind, so dass gilt: DBmax ≤ LS ≤ 2,5 x DBmax.It is also advantageous that 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. An embodiment that is advantageous in terms of noise generation is characterized in that the bores have a maximum diameter DBmax and are spaced apart from the respective blade tip over a radial length LS, so that: DBmax≦LS≦2.5×DBmax.

Besonders bevorzugt ist LS=1,5 x DBmax. In anderen Worten sind die Bohrungen vorzugsweise um den 1,5-fachen Bohrungsdurchmesser von der Schaufelspitze nach radial innen versetzt. Gemessen wird auch hier stets im Mittelpunkt der Bohrungen.LS=1.5×DBmax is particularly preferred. In other words, the bores are preferably offset radially inward from the blade tip by 1.5 times the bore diameter. Here, too, measurements are always taken in the center of the bores.

Bezogen auf den maximalen Lüfterraddurchmesser D des Lüfterrads entspricht die Länge LS, mit welcher die Bohrungen von der jeweiligen Schaufelspitze über beabstandet sind, vorzugsweise 1,5% des maximalen Lüfterraddurchmessers D des Lüfterrads.Based on the maximum fan wheel diameter D of the fan wheel, the length LS by 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.

Vorzugsweise sind alle Bohrungen des Lüfterrads bezüglich Form und Größe jeweils identisch ausgebildet.Preferably, all bores of the fan wheel are each identical in terms of shape and size.

In einer vorteilhaften Ausführungsvariante des Axialventilators ist vorgesehen, dass die Bohrungen über eine Erstreckung entlang der Schaufelspitze der jeweiligen Lüfterradschaufel angeordnet sind, welche 10-40% einer maximalen Erstreckung der Schaufelspitze entlang des Kopfspalts entspricht. Das bedeutet, dass es entlang der Schaufelspitze einen überwiegenden Abschnitt gibt, in dem keine Bohrungen vorgesehen sind, jedoch eine Mindestmenge und eine Mindesterstreckung nicht zu unterschreiten sind. Ferner ist günstig, die Bohrungen insbesondere in einem Bereich der Schaufelspitze anzuordnen, der an die jeweilige Schaufelvorderkante und/oder jeweilige Schaufelhinterkante angrenzt. Soweit die Lüfterradschaufeln im Übergangsbereich von der Schaufelspitze zur Schaufelvorderkante oder jeweilige Schaufelhinterkante radial eingezogen verlaufen und in diesem Abschnitt kein Kopfspalt zu dem Gehäuse mehr besteht, können Bohrungen gleichwohl auch in diesem Abschnitt entlang der Schaufelspitze vorgesehen werden.In an advantageous embodiment variant of the axial fan, it is provided that 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 to arrange the bores in particular in a region of the blade tip which adjoins the respective front edge and/or the respective rear edge of the blade. As far as the fan blades in the The transition area from the blade tip to the blade front edge or the respective blade rear edge is drawn in radially and there is no longer a head gap to the housing in this section, bores can nevertheless also be provided in this section along the blade tip.

Der Axialventilator sieht erfindungsgemäß vor, dass jede der Lüfterradschaufeln entlang der Schaufelspitze jeweils einen sich an eine radiale Mittellinie der Lüfterradschaufeln beidseitig angrenzenden Mittelabschnitt aufweist, der frei von Bohrungen ist. Die Bohrungen werden somit in einem Bereich der Vorderkante und Hinterkante der Lüfterradschaufeln vorgesehen. Der Mittelabschnitt bestimmt 20-90%, weiter bevorzugt 40-80% der maximalen Erstreckung der jeweiligen Lüfterradschaufel in Umfangsrichtung.According to the invention, 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.

In einer Weiterbildung des Axialventilators sind die Bohrungen zusätzlich entlang der Vorderkante und der Hinterkante der Lüfterradschaufeln vorgesehen. Die Abstände zueinander bzw. zur Vorderkante und/oder einer Hinterkante entsprechen dabei vorzugsweise denjenigen der Bohrungen entlang der Schaufelspitze bzw. zu der Schaufelspitze.In a development of the axial fan, the bores are additionally provided along the front edge and 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.

Ferner ist eine Ausführung günstig, bei welcher bei dem Axialventilator die jeweilige Anzahl der Bohrungen zusätzlich entlang der Vorderkante und der Hinterkante der Lüfterradschaufeln kleiner oder gleich der Anzahl an Bohrungen entlang der Schaufelspitze ist. Das bedeutet, dass die Anzahl der Bohrungen an der Vorderkante und an der Hinterkante jeweils stets nicht größer ist, als die Anzahl der Bohrungen an der Schaufelspitze.Furthermore, an embodiment is favorable in which, in the case of the axial fan, the respective number of bores along the front edge and 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.

Der Axialventilator ist in einer Ausführung ferner dadurch gekennzeichnet, dass das Lüfterrad reversierbar ausgebildet und seine im Betrieb erzeugte Strömungsrichtung von seiner Rotationsrichtung abhängt. Dann werden die Bohrungen vorzugsweise sowohl an der Vorderkante als auch der Hinterkante sowie an beiden axialen Seiten der jeweiligen Lüfterradschaufeln vorgesehen.In one embodiment, the axial fan is further characterized in that the fan wheel is designed to be reversible and its direction of flow generated during operation depends on its direction of rotation. Then the holes are preferably both on the leading edge and the trailing edge and provided on both axial sides of the respective fan blades.

Andere vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet und werden nachstehend zusammen mit der Beschreibung der bevorzugten Ausführung der Erfindung anhand der Figuren näher dargestellt. Es zeigen:

Fig. 1
eine Draufsicht auf einen Axialventilator in einer ersten Ausführung;
Fig. 2
eine Detailansicht des Axialventilators aus Figur 1;
Fig. 3
eine perspektivische Vorderansicht des Axialventilators aus Figur 1;
Fig. 4
eine perspektivische Rückansicht des Axialventilators aus Figur 1;
Fig. 5
eine Draufsicht auf einen Axialventilator in einer zweiten Ausführung.
Other advantageous developments of the invention are characterized in the dependent claims and are presented in more detail below together with the description of the preferred embodiment of the invention with reference to the figures. Show it:
1
a plan view of an axial fan in a first embodiment;
2
a detailed view of the axial fan figure 1 ;
3
a perspective front view of the axial fan of Figure 1;
4
a perspective rear view of the axial fan of Figure 1;
figure 5
a plan view of an axial fan in a second embodiment.

In den Figuren 1 - 4 ist eine erste Ausführungsvariante des Axialventilators 1 gezeigt. Dieser umfasst ein ringförmig geschlossenes Gehäuse 2, in dem das reversierbare ausgebildete Lüfterrad 3 zur Erzeugung des Axialluftstromes angeordnet ist, dessen Strömungsrichtung von der Rotationsrichtung des Lüfterrads 4 abhängt. Das Lüfterrad 3 weist die Nabe 5 mit mehreren in Kreisform angeordneten Belüftungsöffnungen 25 auf, in der der Antriebsmotor aufgenommen ist, welcher über die Anschlüsse 14 elektrisch versorgt wird. Rückseitig ist der Antriebsmotor von der Halterung 20 gehalten, welche über in Umfangsrichtung verteilt angeordnete Stege 11 mit dem Gehäuse 2 verbunden ist. Die Stege 11 verlaufen geradlinig, sind jedoch gegenüber einer Radialebene geneigt. Von der Nabe 5 aus erstrecken sich die Lüfterradschaufeln 4 nach radial außen bis zu ihrer jeweiligen Schaufelspitze 8, welche die an die Innenwand des Gehäuses 2 angrenzende Schaufelkante bildet. Zwischen den Schaufelspitzen 8 und der Innenwand des Gehäuses 2 ist der Kopfspalt 12 vorgesehen, so dass das Lüfterrad 3 gegenüber dem Gehäuse 2 rotieren kann. Die Lüfterradschaufeln 4 sind jeweils identisch geformt. Angrenzend zur Schaufelspitze 8 weisen sie in Umfangsrichtung gesehen beidseitig jeweils einen radial eingezogenen Abschnitt 9 auf, in dem die Schaufelkante zwar noch nach radial außen weist, jedoch von der Innenwand des Gehäuses 2 beabstandet ist. Anschließend geht die Schaufelkante in die Vorderkante 17 und Hinterkante 18 über, welche jeweils in Umfangsrichtung weisen, jedoch gegenüber dem radial äußersten Abschnitt der Lüfterradschaufel 4 jeweils in Umfangsrichtung eingezogen gestaltet sind. Entlang ihrer jeweils in Umfangsrichtung gesehenen Mittelachse ist an den Lüfterradschaufeln 4 jeweils eine axiale Stufe 24 ausgebildet, die sich nach radial innen gesehen vergrößert und zur Schaufelspitze 8 hin ausläuft, so dass im Bereich der Schaufelspitze 8 ein stufenloser Verlauf der Laufradschaufel 4 gegeben ist.In the Figures 1 - 4 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 supplied via the connections 14 . At the rear, 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 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 merges 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.

An jeder der Lüfterradschaufeln 4 sind entlang der jeweiligen Schaufelspitze 8 auf beiden axialen Seiten mehrere Bohrungen 7 mit kreisförmigem Querschnitt vorgesehen. Die Bohrungen 7 sind auf beiden axialen Seiten an der jeweils identischen Position ausgebildet und weisen somit die jeweils identische Mittelachse auf. Bevorzugt wird vorgesehen, die Bohrungen 7 als Durchgangsbohrungen zu gestalten. In der Ausführung gemäß der Figuren 1 - 4 sind auf beiden zur Vorderkante 17 und zur Hinterkante 18 weisenden Endabschnitten entlang der Schaufelspitze 8 jeweils acht Bohrungen 7, d.h. pro Lüfterradschaufel 4 insgesamt 16 Bohrungen 7 vorgesehen, von denen sich pro Bereich mit Bohrungen 7 jeweils sechs Bohrungen 7 entlang der Schaufelspitze 8 entlang des Kopfspalts 12 und jeweils zwei Bohrungen 7 im eingezogenen Abschnitt 9 befinden. In der Ausführung gemäß Figur 5 sind an den jeweiligen Endabschnitten entlang der Schaufelspitze 8 jeweils nur sieben Bohrungen 7, d.h. pro Lüfterradschaufel 4 insgesamt 14 Bohrungen 7 vorgesehen. Gegenüber der Ausführung gemäß Figur 1 - 4 sind bei der Ausführung gemäß Figur 5 die Bohrungen 7 in Umfangsrichtung gesehen weiter nach außen verlagert, so dass sich vier der sieben Bohrungen 7 jeweils entlang der Schaufelspitze 8 entlang des Kopfspalts 12 und jeweils drei Bohrungen 7 im eingezogenen Abschnitt 9 befinden. Im Übrigen sind die Ausführungen gemäß Figur 1-4 und Figur 5 identisch. In beiden Ausführungen nicht gezeigt, gleichwohl ebenfalls vorsehbar sind entsprechende Bohrungen 7 im Bereich der Vorderkante 17 und der Hinterkante 18 sowie sowohl an der Vorderkante 17 als auch der Hinterkante 18 der jeweiligen Lüfterradschaufeln 4. Die Anzahl der Bohrungen jeweils entlang der Vorderkante 17 bzw. der Hinterkante 18 wird jedoch geringer festgelegt als diejenige der radialen Außenkante. Jede der Lüfterradschaufeln 4 umfasst entlang der Schaufelspitze 8 jeweils einen sich an eine radiale Mittellinie der Lüfterradschaufeln 4 beidseitig angrenzenden Mittelabschnitt 15 auf, der frei von Bohrungen 7 ist. Der Mittelabschnitt 15 ohne Bohrungen 7 bestimmt in beiden Ausführungen gemäß der Figuren 1 und 5 den vergleichsweise größeren Bereich, d.h. über eine größere Erstreckung der jeweiligen Lüfterradschaufel 4 sind keine Bohrungen 7 vorgesehen, da sich diese im Wesentlichen in den Umfangsrandabschnitten befinden.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. Provision is preferably made for the bores 7 to be in the form of through bores. In the execution according to Figures 1 - 4 eight bores 7 are provided on the two end sections pointing towards the front edge 17 and the rear edge 18 along the blade tip 8, i.e. a total of 16 bores 7 per fan wheel 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 holes 7 in the retracted section 9 are located. In execution according to figure 5 only seven bores 7 are provided on the respective end sections along the blade tip 8 , ie a total of 14 bores 7 per fan wheel blade 4 . Compared to the execution according to Figure 1 - 4 are in accordance with the execution figure 5 the bores 7 are shifted further outwards as seen in the circumferential direction, so that four of the seven bores 7 are located along the blade tip 8 along the head gap 12 and three bores 7 are located in the drawn-in section 9 . Otherwise, the statements according to Figure 1-4 and figure 5 identical. Not shown in both versions, but corresponding bores 7 can also be provided in the area of the front edge 17 and the rear edge 18 and both on the front edge 17 and the rear edge 18 of the respective fan wheel blades 4. The number of bores along the front edge 17 or the However, trailing edge 18 is set less than that of the radially outer edge. 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.

In beiden Ausführungen der Figuren 1 und 5 weisen die Lüfterradschaufeln 4 gegenüber der sich durch das Gehäuse 2 erstreckenden Axialebene einen sehr geringen Anstellwinkel weniger als 25° auf, der gut in Figur 3 zu erkennen ist. Bei derartig geringen Anstellwinkeln sind die Bohrungen 7 besonders wirkungsvoll.In both versions of the figures 1 and 5 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 7 are particularly effective.

Die Größe, Form und Anordnung der Bohrungen 7 beeinflusst den geräuschmindernden Effekt deutlich. In Figur 5 sind vorteilhafte Dimensionierungen eingetragen, welche identisch auch für das Ausführungsbeispiel der Figuren 1-4 anwendbar sind. Die Bohrungen 7 weisen einen maximalen Durchmesser DBmax auf, der 1% des maximalen Lüfterraddurchmessers D des Lüfterrads 4 entspricht, gemessen jeweils im Mittelpunkt der Bohrungen 7. Der Abstand A der Bohrungen 7 zueinander entlang der jeweiligen Schaufelspitze 8 entspricht dem doppelten maximalen Durchmesser DBmax und 2% des maximalen Lüfterraddurchmessers D des Lüfterrads 4. Von der Schaufelspitze 8 sind die Bohrungen 7 über die Länge LS beabstandet, welche 1,5% des Laufraddurchmessers D und dem 1,5-fachen des maximalen Durchmessers DBmax ausmacht. Die radial außen liegende Schaufelspitze 8 der jeweiligen Lüfterradschaufel 4 verläuft durchgängig und ununterbrochen. Gemäß der Ausführung in Figur 5 erfolgt die Verteilung der Bohrungen 7 entlang der Schaufelspitze 8 über eine Länge, welcher 10% der Schaufelspitzenlänge L entspricht, entlang derer der Kopfspalt 12 gebildet ist. In der Ausführung gemäß der Figuren 1 - 4 sind es 20%.The size, shape and arrangement of the holes 7 influences the noise-reducing effect significantly. In figure 5 are entered advantageous dimensions, which are identical for the embodiment of Figures 1-4 are applicable. The holes 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 fan wheel diameter D of the Fan wheel 4. The holes 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. According to the implementation in figure 5 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%.

In beiden Ausführungen gemäß der Figuren 1-4 und 5 sind alle Bohrungen 7 jeweils identisch ausgebildet. Alternativ kann jedoch auch vorgesehen werden, dass sich die Bohrungen 7 zueinander in Form und Größe unterscheiden. In both versions according to the Figures 1-4 and 5 all bores 7 are identical in design. Alternatively, however, it can also be provided that the bores 7 differ from one another in terms of shape and size.

Claims (15)

  1. An axial fan (1) with a housing (2) and a fan wheel (3) that is arranged in the housing (2) for the purpose of generating an axial air flow through the housing (2), wherein the fan wheel (3) has a plurality of fan wheel blades (4) which extend radially on the outside from a hub (5) to the respective blade tip (8) and are spaced apart from an inner wall of the housing (2) by a head gap (12), wherein each of the fan wheel blades (4) has along the blade tip (8) a middle portion (15) which adjoins a radial center line of the fan wheel blades (4) and is free of boreholes (7), and wherein the middle portion defines 20-90% of an extent of the respective fan wheel blade (4) in the circumferential direction, characterized in that the fan wheel blades (4) have a plurality of boreholes (7) along the respective blade tip (8) in the vicinity of both a front edge (17) and rear edge (18) of the fan wheel blades (4).
  2. The axial fan as set forth in claim 1, characterized in that the fan wheel blades (4) have a small angle of attack relative to an axial plane in the range of 5-25°, particularly 10-20°.
  3. The axial fan as set forth in claim 1 or 2, characterized in that the boreholes (7) are formed on both axial sides of the fan wheel blades (4).
  4. The axial fan as set forth in claim 1 or 2, characterized in that the boreholes (7) are embodied as through holes through the fan wheel blades (4).
  5. The axial fan as set forth in any one of the preceding claims, characterized in that the number of boreholes (7) per fan blade (4) along the respective blade tip (8) is at least five, and the boreholes (7) are arranged along a line parallel to the blade tip (8).
  6. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) have a circular cross section.
  7. The axial fan as set forth in the preceding claim, characterized in that the boreholes (7) have a maximum diameter DBmax which corresponds to 1% of a maximum fan wheel diameter D of the fan wheel (3),
  8. The axial fan as set forth in the previous claim, characterized in that the boreholes (7) are situated at a distance A from one another along the respective blade tip (8) which corresponds to twice the maximum diameter DBmax, the distance being measured at the center point of the respective borehole (7).
  9. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) are situated at a distance A from one another along the respective blade tip (8) which corresponds to 2% of a maximum fan wheel diameter D of the fan wheel (3).
  10. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) have a maximum diameter DBmax and are spaced apart from the respective blade tip (8) over a length LS, so that the following applies:
    DBmax ≤ 5 LS ≤ 2.5 x DBmax, particularly LS=1.5 x DBmax,
  11. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) are spaced apart from the respective blade tip (8) over a length LS which corresponds to 1.5% of a maximum fan wheel diameter D of the fan wheel.
  12. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) are provided over an extent along the blade tip (8) of the respective fan wheel blade (4) which is equivalent to 10-40% of a maximum extent of the blade tip (8) along the head gap.
  13. The axial fan as set forth in any one of the preceding claims, characterized in that the boreholes (7) are additionally provided along the front edge (17) and the rear edge (18) of the fan wheel blades (4).
  14. The axial fan as set forth in the previous claim, characterized in that a respective number of boreholes (7) along the front edge (17) and the rear edge (18) of the fan wheel blades is less than or equal to a number of boreholes (7) along the blade tip (8),
  15. The axial fan as set forth in any one of the preceding claims, characterized in that the fan wheel (3) is designed to be reversible, and the direction of flow generated during operation depends on the direction of rotation thereof.
EP21215518.8A 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores Active EP3988797B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019105190.8A DE102019105190A1 (en) 2019-02-28 2019-02-28 Axial fan with noise-reducing fan blades
EP20155642.0A EP3702620B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP20155642.0A Division-Into EP3702620B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores
EP20155642.0A Division EP3702620B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores

Publications (2)

Publication Number Publication Date
EP3988797A1 EP3988797A1 (en) 2022-04-27
EP3988797B1 true EP3988797B1 (en) 2022-11-23

Family

ID=69379900

Family Applications (2)

Application Number Title Priority Date Filing Date
EP21215518.8A Active EP3988797B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores
EP20155642.0A Active EP3702620B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP20155642.0A Active EP3702620B1 (en) 2019-02-28 2020-02-05 Axial fan with noise reducing fan impeller vanes having bores

Country Status (6)

Country Link
US (1) US11391282B2 (en)
EP (2) EP3988797B1 (en)
KR (1) KR102320943B1 (en)
CN (1) CN210050072U (en)
DE (1) DE102019105190A1 (en)
PL (2) PL3702620T3 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD972706S1 (en) * 2019-02-28 2022-12-13 Ebm-Papst St. Georgen Gmbh & Co. Kg Ventilating fan
DE102019105355B4 (en) * 2019-03-04 2024-04-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Fan wheel of an axial fan
USD972707S1 (en) * 2019-04-29 2022-12-13 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilating fan
DE102021116749A1 (en) 2021-06-29 2022-12-29 Stiebel Eltron Gmbh & Co. Kg Decentralized ventilation unit and flow straightener

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3716718A1 (en) * 1986-05-19 1987-11-26 Usui Kokusai Sangyo Kk LOW SPEED PROPELLER FANS
JPH11201090A (en) * 1998-01-13 1999-07-27 Daikin Ind Ltd Runner for blower
JP3008930B2 (en) * 1998-06-23 2000-02-14 ダイキン工業株式会社 Impeller for blower
JP3746647B2 (en) * 1999-11-12 2006-02-15 タナカ工業株式会社 Engine blower
US20050186070A1 (en) * 2004-02-23 2005-08-25 Ling-Zhong Zeng Fan assembly and method
JP2005240749A (en) * 2004-02-27 2005-09-08 Mitsubishi Electric Corp Blower
DE102008052981A1 (en) * 2008-10-23 2010-04-29 Mtu Aero Engines Gmbh Guide vane for axial compressor of turbomachine, has through-hole provided with respect to flow direction of fluid to be compressed to downstream side of radial edge region, where through-hole takes up pointed angle to central plane
CN101440822A (en) * 2008-11-28 2009-05-27 中山大洋电机股份有限公司 Axial-flow fan and fan blade of centrifugal fan
GB0910838D0 (en) * 2009-06-24 2009-08-05 Rolls Royce Plc A shroudless blade
US20120100001A1 (en) * 2010-10-20 2012-04-26 Zaward Corporation Fan structure
US9909505B2 (en) * 2011-07-05 2018-03-06 United Technologies Corporation Efficient, low pressure ratio propulsor for gas turbine engines
CN102635572A (en) * 2012-04-27 2012-08-15 浙江理工大学 Blade perforated small axial fan
CN102705264A (en) * 2012-06-15 2012-10-03 美的集团有限公司 Axial flow wind wheel
DE102014102311A1 (en) * 2014-02-21 2015-08-27 Ebm-Papst St. Georgen Gmbh & Co. Kg Fan with a paddle wheel
CN204242077U (en) * 2014-10-30 2015-04-01 烟台职业学院 New-type computer fan
CN104454641B (en) * 2014-11-13 2017-06-16 中国北车集团大连机车研究所有限公司 Electric express locomotive cooling system low noise axial flow fan vane wheel
CN107313979B (en) * 2017-08-31 2019-04-30 广东美的制冷设备有限公司 Axial-flow windwheel and air conditioner with it
CN107489658A (en) * 2017-08-31 2017-12-19 中国航天空气动力技术研究院 Electric fan noise-reduction method and improved blade of electric fan structure based on blade remodeling
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 (en) * 2018-10-30 2020-05-07 주식회사 명성 Safety net for fan

Also Published As

Publication number Publication date
CN210050072U (en) 2020-02-11
PL3702620T3 (en) 2022-08-16
US20200277962A1 (en) 2020-09-03
EP3702620B1 (en) 2022-04-27
DE102019105190A1 (en) 2020-09-03
US11391282B2 (en) 2022-07-19
KR20200105627A (en) 2020-09-08
PL3988797T3 (en) 2023-03-06
EP3988797A1 (en) 2022-04-27
KR102320943B1 (en) 2021-11-04
EP3702620A1 (en) 2020-09-02

Similar Documents

Publication Publication Date Title
EP3988797B1 (en) Axial fan with noise reducing fan impeller vanes having bores
EP2025945B1 (en) Flow working machine with ring canal wall fitting
DE102008011644A1 (en) Housing structuring for axial compressor in the hub area
EP3298284B1 (en) Flat flow-conducting grille
DE102007056953B4 (en) Turbomachine with Ringkanalwandausnehmung
EP0916812A1 (en) Final stage for an axial turbine
EP3705728A1 (en) Housing for a turbomachine, in particular for a radial fan
DE102008052401A1 (en) Turbine working machine with running column feeder
DE602004008811T2 (en) Axial
EP3942184A1 (en) Barrel casing pump and method for manufacturing a barrel casing pump
DE102004023270A1 (en) An axial flow fan
DE60019965T2 (en) AXIAL TURBINE FOR GASES
EP2410131A2 (en) Rotor of a turbomachine
EP3473808B1 (en) Blade for an internally cooled turbine blade and method for producing same
EP3181813B1 (en) Center-of-gravity threading of rotor blades
EP3114354A1 (en) Fan wheel of an axial fan
EP1371813A1 (en) Blading of a turbomachine
DE202019101166U1 (en) Axial fan with noise reducing fan blades
EP3865711A1 (en) Fan with cover plate on the rotor bell
DE102019108811B4 (en) Rotor blade of a turbomachine
EP3596341A1 (en) Fan
EP4063663A1 (en) Bladeless flow diffuser
EP4063664A1 (en) Fan wheel of an axial fan
EP3877653B1 (en) Multi-stage hydraulic machine
CH650563A5 (en) Diffuser in a centrifugal driven machine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AC Divisional application: reference to earlier application

Ref document number: 3702620

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20220518

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20220720

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTC Intention to grant announced (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

INTG Intention to grant announced

Effective date: 20220915

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AC Divisional application: reference to earlier application

Ref document number: 3702620

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502020002073

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1533289

Country of ref document: AT

Kind code of ref document: T

Effective date: 20221215

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20230216

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230323

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230223

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 20230220

Year of fee payment: 4

Ref country code: FR

Payment date: 20230221

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230323

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230224

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PL

Payment date: 20230113

Year of fee payment: 4

Ref country code: IT

Payment date: 20230228

Year of fee payment: 4

Ref country code: BE

Payment date: 20230216

Year of fee payment: 4

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230424

Year of fee payment: 4

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502020002073

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230228

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230228

26N No opposition filed

Effective date: 20230824

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20221123

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230205

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 20240220

Year of fee payment: 5