EP0942175B1 - Zentrifugalgebläse, herstellungsverfahren dafür sowie klimaanlage mit einem solchem gebläse - Google Patents

Zentrifugalgebläse, herstellungsverfahren dafür sowie klimaanlage mit einem solchem gebläse Download PDF

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Publication number
EP0942175B1
EP0942175B1 EP98944261A EP98944261A EP0942175B1 EP 0942175 B1 EP0942175 B1 EP 0942175B1 EP 98944261 A EP98944261 A EP 98944261A EP 98944261 A EP98944261 A EP 98944261A EP 0942175 B1 EP0942175 B1 EP 0942175B1
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EP
European Patent Office
Prior art keywords
hub
vanes
vane
centrifugal blower
molding
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Expired - Lifetime
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EP98944261A
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English (en)
French (fr)
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EP0942175A1 (de
EP0942175A4 (de
Inventor
Tsunehisa-Kanaoka-Kojo-Daikin Indust. Ltd. Sanagi
Hideaki-Kanaoka-Kojo-Daikin Indust. Ltd. Sakamoto
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • F04D29/661—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • 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
    • F05D2240/304—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 trailing edge of a rotor blade

Definitions

  • the present invention relates to a centrifugal blower featuring a vaned structure and a method of fabricating the same, and to an air conditioning apparatus including the centrifugal blower.
  • a centrifugal blower includes an impeller consisting of a hub rotatably mounted around a rotary shaft of a motor, a shroud disposed at a given distance from and in opposed relation to the hub, and a plurality of vanes extending between the outer periphery of the hub and the outer periphery of the shroud and arranged around and generally radially from the axis of the hub. According to such arrangement, air currents flowing from the front edge side of the vanes to the rear edge side thereof are produced by rotation of the impeller.
  • Such a centrifugal blower has a suction port provided at a portion forming the axis of the impeller so that the air sucked through the suction port is blown around the impeller from a blow-off port provided on the outer periphery of the impeller.
  • a mode of air suction and blow off will match the mode of air circulation required of a room air conditioner and, more particularly, a ceiling embedded type or hanger type air conditioner (that is, an air circulation mode such that after room air sucked from a center portion of a room is conditioned, the conditioned air is blown out over the whole room area). Therefore, a centrifugal blower is often employed as a blower for room air conditioners.
  • the pressure difference between a pressure surface and a negative pressure surface in a vane which performs air supply work is larger as compared to the pressure differences in the case of other types of blowers, such as axial blowers. Therefore, as the impeller rotates, the pressure gradient at the rear edge portion is large enough to cause so much velocity loss in the air current flow in such a case that a high pressure air current flowing along the pressure surface side of the vane from the front edge of the vane toward the rear edge thereof and a low pressure air current flowing along the negative pressure surface side of the vane from the front edge of the vane toward the rear edge thereof meet with each other adjacent the rear edge of the vane, so that the joined air currents are equilibrated to a specified pressure.
  • the rear edge configuration of a vane is generally such that the rear edge portion linearly extends widthwise of the vane; therefore, such velocity losses will simultaneously occur all over the whole area of the rear edge portion of the vane.
  • blast noise reduction has been highly required of centrifugal blowers and various means intended to meet this requirement have been proposed.
  • none of the proposals for blast noise reduction have been found satisfactory. The requirement for such noise reduction is particularly high with respect to a room air conditioner including a centrifugal air conditioning blower which is to be set in a room.
  • a centrifugal blower according to the preamble of claim 1 is known from GB-A-2 105 751 or US-A-5,558,499.
  • the centrifugal blower in accordance with the present invention includes an impeller having a hub rotatably mounted around a rotary shaft of a motor, a shroud disposed at a specified distance from the hub and in opposed relation thereto, the shroud being formed with a suction port at a portion defining the axis of the hub, and a plurality of vanes extending between the outer periphery of the hub and the outer periphery of the shroud and arranged generally radially around the axis of the hub, so that air currents flowing from the front edge side of the vanes toward the rear edge side of the vanes are produced by rotation of the impeller, wherein rear edges of the vanes have a saw teeth configuration zigzagged in the longitudinal direction of the vane and extending widthwise of the vane, and the further features recited in claim 1.
  • each vane has a saw teeth shape with teeth zigzagged in the longitudinal direction of the vane and extending widthwise of the vane. Therefore, in the rear edge portion a longer vane portion and a shorter vane portion exist in alternate relation, so that a combined air current flow resulting from the meeting of air current flowing along the pressure surface side with air current flowing along the negative pressure surface side is gradually performed stepwise over the entire length of the rear edge.
  • the construction of the molding tool is simplified as compared to the case in which the teeth are configured to have a complex polygonal shape, for example, and this provides a favorable effect such that cost reduction can be achieved so much in the fabrication of the centrifugal blower.
  • tip portions of the plurality of teeth of triangular shape are each configured to have a planar or arcuate shape, the tip portions are less liable to damage due to cracking or the like as compared to the case in which the tip portions are sharp-edged, for example, and this provides for so much improvement in the durability of the centrifugal blower.
  • the teeth of the saw teeth configuration are designed to meet the condition of 0.005 ⁇ H/D ⁇ 0.015 and the condition of 0.01 ⁇ S/D ⁇ 0.02 in relation to the outer diameter "D" of the impeller, where "H” is tooth height and “S” is tooth pitch.
  • the present invention also provides a method of fabricating aforesaid centrifugal blower.
  • an integrally molded component comprising a hub and vanes as constituent parts of an impeller which are integrated together is first fabricated, and then a shroud molded separately from the integrally molded component is fixedly joined to ends of the vanes, the impeller being thus obtained.
  • the integrally molded component is fabricated by carrying out the steps of:
  • the present invention makes it possible to easily form aforesaid saw teeth configuration merely by changing the direction of die releasing with respect to third molding dies for forming of saw teeth configuration to the longitudinal direction of the vanes.
  • the present invention makes it possible to easily fabricate aforesaid molded component, which in turn facilitates fabrication of aforesaid impeller and, in effect, makes it possible to provide a less expensive centrifugal blower.
  • the present invention provides an air conditioning apparatus using the centrifugal blower as an air conditioning blower of the invention.
  • the characteristic effect of the centrifugal blower that is, high noise attenuation performance is reflected as it is in the operating performance of the air conditioning apparatus, it being thus possible to provide an air conditioning apparatus having high noise attenuation characteristic.
  • Such noise attenuation effect is especially remarkable in case where the air conditioning apparatus is a room air conditioner to be set in a room.
  • Fig. 1 shows an impeller 10 of a centrifugal blower X embodying the present invention.
  • Fig. 2 shows a room air conditioner Z including the centrifugal blower X.
  • the centrifugal blower X consists of a motor 19 and an impeller 10 to be driven to rotate by the motor 19.
  • the impeller 10 includes a hub 11 consisting of a center portion 11a of generally conical shape, a flat plate-like flange 11b, and a mounting portion 11c rotatably mounted to a motor shaft 19a of the motor 19, a shroud 12 disposed a given distance apart from the hub 11 in opposed relation thereto and centrally formed with an air suction port 16, and a plurality of vanes 13 extending on the outer periphery of the hub 11, more specifically, between the outer periphery of the flange 11b and the outer periphery of the shroud 12, and radially arranged at circumferentially equal intervals.
  • an air supply opening 17 is defined between the hub 11 and the outer periphery of the shroud 12, and an air flow path 18 is defined by a passage extending from the air suction port 16 to the air supply opening 17.
  • the hub 11 is a structure formed from a disc plate of a specified diameter by compression molding the disc plate thicknesswise thereof in the vicinity of the center of the disc plate and, as will be described hereinafter, the hub 11, together with vanes 13, is integrally formed by compression molding of resin material.
  • the shroud 12 is an annular structure having an arcuate sectional configuration and is formed by compression molding of resin material separately from the hub 11 and the like. After having been molded, the shroud 12 is fixedly joined to an integrally molded structure 15 consisting of the hub 11 and vanes 13 (see Figs. 5 and 6).
  • the vanes 13 are each a plate member having a curved streamline shape and are arranged radially in plurality (8 vanes in the present embodiment) across the space between the outer periphery of the hub 11 and the outer periphery of the shroud 12 and at circumferentially equal intervals.
  • the vanes 13 are integrally molded with the hub 11 by compression molding of resin material.
  • the vane 13 has a most important characteristic feature in the construction of its rear edge 13b.
  • the rear edge 13b of vane 13 is configured, instead of being linear as in the past, to have a saw teeth shape 20 such that the rear edge 13b is alternately bent i.e. zigzagged in the longitudinal direction of the vane and extending widthwise of the vane.
  • the saw teeth shape 20 consists of teeth 21 disposed in succession along the rear edge 13b, as Figs.
  • the shape of tooth is trapezoidal with its front end made to have a linear shape instead of a triangular shape, and dimensions of tooth 21 are set to meet the condition of 0.005 ⁇ H/D ⁇ 0.015 and the condition of 0.01 ⁇ S/D ⁇ 0.02 in relation to the outer diameter "D" of the impeller 10, where "H” is tooth height and "S” is tooth pitch.
  • the tip portion 21a of tooth 21 is arcuate as shown in Fig. 4; but alternately, it may be planar.
  • the hub 11 and vanes 13 are integrally molded (into an integrally molded member 15) from among component members of the impeller 10, namely, the hub 11, the shroud 12, and a plurality of vanes 13. Whilst, the shroud 12 is molded separately from the integrally molded member 15. After these members having been molded, the shroud 10 is joined to the integrally molded member 15 (by deposition joining or adhesive jointing) into an integral structure. Such a fabricating procedure is already known in the art.
  • a rear edge of a vane is of a straight line shape. Therefore, fabrication of an integrally molded member by compression molding can be easily carried out by using a pair of molding dies (for example, an upper die and a lower die) disposed in opposed relation and adapted to be movable toward and away from each other.
  • the rear edge 13b of the vane 13 has the saw teeth configuration 20; therefore, it is impossible to form such an integrally molded structure 15 having vanes 13 and hub 11 integrally combined together by using the above mentioned molding dies, due to difficulty in die release operation of the saw teeth shape portion 20.
  • the fabricating method of the invention is employed in forming the integrally molded structure 15 by using three kinds of dies (that is, a lower die 31 and an upper die 32, and a plurality of cutting dies 33).
  • the lower die 31 is a molding die including a hub interior molding surface 31a for forming the surface on which the vanes 13 of the integrally molded structure 15 are arranged, a vane molding surface 31b for forming the front edge 13a of the vane 13, and a cutting die fitting portion 31c for providing a space for insertion of a cutting die 33 to be described hereinafter.
  • This lower die 31 corresponds to "first molding die” as defined in the accompanying claims.
  • the upper die 32 is a molding die including a hub exterior molding surface 32a for forming the surface on which vanes 13 of the integrally molded structure 15 are not disposed.
  • This upper die 32 corresponds to "second molding die” as defined in the accompanying claims.
  • the cutting die 33 is a molding die disposed between adjacent vanes 13 in the integrally molded structure 15 and includes a saw teeth forming surface 33a for forming the saw teeth configuration 20, and a vane forming surface 33b for forming the rear edge 13b side portion of the vane 13.
  • This cutting die 33 corresponds to "third molding die” as defined in the accompanying claims.
  • the upper die 32 is disposed above the hub interior molding surface 31a of the lower die 31, with its hub exterior molding surface 32a oriented toward the lower die 31, the upper die 32 being enabled to move toward and away from the lower die 31 and in opposite directions.
  • the cutting dies 33 are arranged so as to be positioned between the lower die 31 and the upper die 32 from a direction perpendicular to the direction in which the lower die 31 and the upper die 32 are positioned in opposed relation, and between adjacent vanes 13 in the integrally molded structure 15 to be molded by each respective cutting die 33.
  • the molding dies 31, 32 33 are released.
  • the upper die 32 is released in a direction in which it is moved away from the lower die 31.
  • Release of the cutting dies 33 is carried out by moving them laterally in the longitudinal direction of the vane 13.
  • the rear edge 13b of each vane 13 of the impeller 10 is configured to have a saw teeth shape 20. Therefore, when air blowing is carried out by driving the motor 19 to rotate the impeller 10, the noise level of the air blowing is low as compared to that in the case of the prior art (i.e., the rear edge 13b of the vane 13 having a linear configuration), high noise attenuation effect being thus obtained.
  • each vane 13 has a saw teeth configuration 20 such that a longer vane portion and a shorter vane portion alternately exist in the rear edge 13b. Therefore, a combined air current flow resulting from meeting at the rear edge 13b of air current flowing along the pressure surface side of the vane 13 with air current flowing along the negative pressure surface side gradually takes place stepwise over the entire length of the rear edge 13b. As a consequence, pressure gradient and velocity loss of air current are reduced due to the meeting of air currents at the rear edge 13b, and air current turbulence at the rear edge 13b is restrained so much, with the result that air blast noise is reduced accordingly.
  • each tooth 21 in the saw teeth configuration 20 by setting dimensions of each tooth 21 in the saw teeth configuration 20 to meet the condition of "0.005 ⁇ H/D ⁇ 0.015" and the condition of "0.01 ⁇ S/D ⁇ 0.02" in relation to the outer diameter "D" of the impeller 10, where tooth height is designated by “H” and tooth pitch is designated by “S”, it is possible to reduce the noise of air blowing more effectively, thereby further enhancing the attenuation of air blowing noise from the centrifugal blower.
  • Fig. 2 illustrates, in the aforesaid room air conditioner Z including the centrifugal blower X of above described construction, the characteristic effect of the centrifugal blower X, that is, aforesaid noise attenuation performance, is reflected as it is in the operating performance of the room air conditioner Z.
  • the centrifugal blower X it is possible to provide a room air conditioner Z having high noise attenuation performance.
  • the construction of the room air conditioner Z is briefly explained as follows.
  • the room air conditioner Z includes the centrifugal blower X disposed centrally in an air passage 4 in a casing 1, and heat exchanger 5 arranged around the centrifugal blower X.
  • numeral 2 designates a suction port corresponding to an air blowing port 16 of the centrifugal blower X.
  • a bell mouth 8 is disposed in the suction port 2, and beneath the bell mouth 8 there is mounted a suction grill 6 having a filter 7.
  • the centrifugal air conditioner X As the centrifugal air conditioner X is driven to operate, indoor air sucked through the suction port 2 is blown from an air blowing port 17 of the centrifugal blower X toward the heat exchanger 5. The air so blown exchanges heat with a refrigerant circulating through the heat exchanger 5 while the air passes through the heat exchanger 5, and is then blown from the air blowing port 3 into a room to heat or cool the room.
  • the centrifugal blower of the present invention can be utilized as a blower for air conditioning apparatus and can also be used in various application areas for fluid transportation.
  • the air conditioning apparatus of the invention which is equipped with the centrifugal blower can be utilized as a built-in ceiling fixture type or ceiling-mounted hanger type air conditioner for use in various types of buildings.

Claims (5)

  1. Zentrifugalgebläse (X) mit einem Laufrad (10) mit einer Nabe (11), welche drehbar um eine sich drehende Welle (19a) des Motors (19) herum angebracht ist, und mit einem Abdeckblech (12), das in einem bestimmten Abstand von dieser Nabe (11) und ihr gegenüberliegend vorgesehen ist, welches Abdeckblech (12) eine Ansaugöffnung (16) bei einem Bereich aufweist, der eine Achse der Nabe (11) definiert, und wobei sich eine Vielzahl von Schaufeln (13) zwischen einem Außenumfang der Nabe (11) und einem Außenumfang des Abdeckblechs (12) erstrecken und im allgemeinen radial um die Achse der Nabe (11) herum angeordnet sind, so dass von vorderen Kanten (13a) der Schaufeln (13) hin zu hinteren Kanten (13b) der Schaufeln (13) fließende Luftströme durch eine Drehung des Laufrads (10) erzeugt werden,
    wobei die hinteren Kanten (13b) der Schaufeln (13) eine Sägezahn-Konfiguration haben, die zickzackartig in einer Längsrichtung der Schaufel (13) ausgebildet ist und sich der Breite der Schaufel (13) nach erstreckt,
    dadurch gekennzeichnet, dass die Zähne (21) dieser Sägezahn-Konfiguration (20) jeweils so ausgestattet sind, dass sie die Bedingung 0,005 < H/D < 0,015 erfüllen und die Bedingung 0,01 < S/D < 0,02 bezüglich einer Außendurchmessers "D" des Laufrads (10), wobei "H" die Höhe der Zähne und "S" der Abstand der Zähne ist.
  2. Zentrifugalgebläse nach Anspruch 1, worin eine Vielzahl von Zähnen (21), die die Sägezahn-Konfiguration (20) bilden, jeweils so ausgestaltet sind, dass sie eine praktisch dreieckige Gestalt haben.
  3. Zentrifugalgebläse nach Anspruch 2, in welchem Spitzenbereiche der Zähne (21) jeweils so ausgestaltet sind, dass sie eine ebene oder bogenförmige Gestalt haben.
  4. Verfahren zur Herstellung eines Zentrifugalgebläses (X) mit einem Laufrad (10) mit einer Nabe (11), einem in einem bestimmten Abstand von der Nabe (11) und dieser gegenüberliegend vorgesehenen Abdeckblech (12) sowie einer Vielzahl von Schaufeln (13), die sich zwischen einem Außenumfang der Nabe (11) und einem Außenumfang des Abdeckbleches (12) erstrecken, wobei die hinteren Kanten (13b) der Schaufel (13) eine Sägezahn-Konfiguration (20) haben, die zickzack-artig in einer Längsrichtung der Schaufel (13) verläuft und sich der Breite der Schaufel (13) nach erstreckt, mit den folgenden Schritten:
    Vorbereiten einer ersten Gießform (31) zum Ausbilden einer der beiden Seitenflächen der Nabe (11), entlang welcher die Schaufeln (13) angebracht werden sollen, und deren beide Seitenflächen einander in Richtung der Dicke der Nabe (11) gegenüberliegen, einer zweiten Gießform (32) zum Ausbilden der anderen Seitenfläche der Nabe (11), die dazu ausgestaltet ist, sich in Richtung der ersten Gießform (31) und von dieser weg zu bewegen, und einer Vielzahl von dritten Gießformen (33), die in Zwischenräumen zwischen benachbarten Schaufeln (13) platziert sind, so dass sie in einer Längsrichtung der Schaufeln (13) rückwärts und vorwärts beweglich sind, um eine Sägezahn-Konfiguration (20) nach einem der Ansprüche 1 bis 3 auszubilden, die zumindest an einer hinteren Kante (13b) jeder Schaufel (13) vorgesehen werden soll,
    Bringen der ersten (31), der zweiten (32) und der dritten Gießform (33) in vorbestimmte Montagepositionen, um geschmolzenes Material in einen durch diese Gießformen (31, 32, 33) gebildeten Hohlraum einzugießen,
    voneinander Wegbewegen der ersten Gießform (31) sowie der zweiten Gießform (32), um das Lösen der Gießformen auszuführen, und Bewegen jeweiliger dritter Gießformen (33) in Längsrichtung der Schaufeln (13), um ein Lösen der Gießformen auszuführen, so dass eine integral geformte Komponente (15) hergestellt wird, in welche eine Nabe (11) und Schaufeln (13) integriert sind, und
    festes Verbinden des Abdeckbleches (12), das separat von dieser integral ausgeformten Komponente (15) ausgeformt wurde, mit Enden der Schaufeln (13) in der integral geformten Komponente (15), so dass das Laufrad (10) erzeugt wird.
  5. Klimaanlage (Z), gekennzeichnet durch das Zentrifugal-Gebläse (X) nach einem der Ansprüche 1 bis 3 und einen Wärmetauscher (5), die in einem Luftkanal (4) vorgesehen sind, der in einem Gehäuse (1) ausgebildet ist.
EP98944261A 1997-09-30 1998-09-28 Zentrifugalgebläse, herstellungsverfahren dafür sowie klimaanlage mit einem solchem gebläse Expired - Lifetime EP0942175B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP26540197 1997-09-30
JP09265401A JP3092554B2 (ja) 1997-09-30 1997-09-30 遠心送風機及びその製造方法並びに該遠心送風機を備えた空気調和機
PCT/JP1998/004331 WO1999017027A1 (fr) 1997-09-30 1998-09-28 Soufflante radiale, procede de fabrication, et conditionneur d'air equipe de cette soufflante

Publications (3)

Publication Number Publication Date
EP0942175A1 EP0942175A1 (de) 1999-09-15
EP0942175A4 EP0942175A4 (de) 2002-05-08
EP0942175B1 true EP0942175B1 (de) 2004-11-24

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EP98944261A Expired - Lifetime EP0942175B1 (de) 1997-09-30 1998-09-28 Zentrifugalgebläse, herstellungsverfahren dafür sowie klimaanlage mit einem solchem gebläse

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Country Link
EP (1) EP0942175B1 (de)
JP (1) JP3092554B2 (de)
CN (1) CN1133819C (de)
AU (1) AU712784B2 (de)
DE (1) DE69827764T2 (de)
ES (1) ES2234153T3 (de)
HK (1) HK1021556A1 (de)
WO (1) WO1999017027A1 (de)

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WO2016090417A1 (en) * 2014-12-12 2016-06-16 Aireng Pty Ltd Centrifugal fan
WO2016201516A1 (en) * 2015-06-16 2016-12-22 Resmed Limited Impeller with inclined and reverse inclined blades
US11566634B2 (en) 2018-10-31 2023-01-31 Carrier Corporation Arrangement of centrifugal impeller of a fan for reducing noise
EP3832146B1 (de) * 2019-12-06 2023-08-02 LG Electronics Inc. Vorrichtung zur sowohl befeuchtung als auch luftreinigung

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JP2001234888A (ja) * 2000-02-25 2001-08-31 Mitsubishi Heavy Ind Ltd 送風機
DE60134420D1 (de) * 2000-12-04 2008-07-24 Robert Bosch Llc Einstückig ausgebildetes hochleistungszentrifugalgebläse
JP4736252B2 (ja) * 2001-06-28 2011-07-27 ダイキン工業株式会社 多翼送風機の羽根車及びそれを備えた多翼送風機
JP4432865B2 (ja) * 2004-09-30 2010-03-17 ダイキン工業株式会社 送風機の羽根車およびそれを用いた空気調和機
JP4517955B2 (ja) * 2005-06-24 2010-08-04 三菱電機株式会社 貫流送風機用羽根車および空気調和機
KR100719103B1 (ko) 2005-09-26 2007-05-17 주식회사 에어로네트 터보형 후향익 다중 임펠러의 하이브리드 설계방법
JP4973249B2 (ja) 2006-03-31 2012-07-11 ダイキン工業株式会社 多翼ファン
ES2378205B2 (es) * 2007-03-14 2013-02-15 Mitsubishi Electric Corporation Acondicionador de aire.
JP4879318B2 (ja) * 2007-03-14 2012-02-22 三菱電機株式会社 遠心ファン、空気調和機
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CN101377206B (zh) * 2007-08-31 2013-08-07 富准精密工业(深圳)有限公司 扇叶结构及具有该扇叶结构的离心风扇
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US9765788B2 (en) * 2013-12-04 2017-09-19 Apple Inc. Shrouded fan impeller with reduced cover overlap
WO2015099155A1 (ja) * 2013-12-27 2015-07-02 本田技研工業株式会社 インペラ
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JPH11101198A (ja) 1999-04-13
AU9186298A (en) 1999-04-23
EP0942175A1 (de) 1999-09-15
JP3092554B2 (ja) 2000-09-25
CN1241248A (zh) 2000-01-12
DE69827764T2 (de) 2005-12-29
ES2234153T3 (es) 2005-06-16
HK1021556A1 (en) 2000-06-16
DE69827764D1 (de) 2004-12-30
CN1133819C (zh) 2004-01-07
AU712784B2 (en) 1999-11-18
EP0942175A4 (de) 2002-05-08

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