EP1411248B1 - Impulseur pour soufflante centrifuge et soufflante centrifuge dotee dudit impulseur - Google Patents

Impulseur pour soufflante centrifuge et soufflante centrifuge dotee dudit impulseur Download PDF

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Publication number
EP1411248B1
EP1411248B1 EP02738677A EP02738677A EP1411248B1 EP 1411248 B1 EP1411248 B1 EP 1411248B1 EP 02738677 A EP02738677 A EP 02738677A EP 02738677 A EP02738677 A EP 02738677A EP 1411248 B1 EP1411248 B1 EP 1411248B1
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EP
European Patent Office
Prior art keywords
impeller
blades
main plate
centrifugal fan
form members
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.)
Expired - Lifetime
Application number
EP02738677A
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German (de)
English (en)
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EP1411248A4 (fr
EP1411248B8 (fr
EP1411248A1 (fr
Inventor
Masahito c/o DAIKIN INDUSTRIES LTD. HIGASHIDA
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.)
Daikin Industries Ltd
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Daikin Industries Ltd
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
Priority claimed from JP2001196177A external-priority patent/JP2003013885A/ja
Priority claimed from JP2001196178A external-priority patent/JP4736252B2/ja
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1411248A1 publication Critical patent/EP1411248A1/fr
Publication of EP1411248A4 publication Critical patent/EP1411248A4/fr
Publication of EP1411248B1 publication Critical patent/EP1411248B1/fr
Application granted granted Critical
Publication of EP1411248B8 publication Critical patent/EP1411248B8/fr
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    • 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
    • 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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • 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

Definitions

  • the present invention relates to an impeller for a centrifugal fan and a centrifugal fan equipped with the same. More particularly, the present invention relates to an impeller for a centrifugal fan in which the ends of a plurality of blades that extend from a main plate are connected by means of an annular side plate, and to a centrifugal fan equipped with the same.
  • a centrifugal fan is employed in devices such as air purifiers, air conditioners, and the like (hereinafter referred to as "air conditioners") in order to blow air.
  • An conventional centrifugal fan known as a multi-blade fan is shown in Figs. 1-3 .
  • Fig. 1 shows lateral cross-sectional views of a conventional multi-blade fan
  • Fig. 2 shows a perspective view of an impeller for the conventional multi-blade fan
  • Fig. 3 shows a plan view of the impeller for the conventional multi-blade fan.
  • the multi-blade fan 10 includes an impeller 13, a casing 11 that covers the impeller 13, and a motor 14 that rotates the impeller 13.
  • the impeller 13 includes a disk-shaped main plate 31 to which one end of each of a plurality of blades 33 are fixed to the outer peripheral edge thereof, and an annular side plate 32 to which the other ends of the blades 33 are connected.
  • An air discharge port 11a, and an air intake port 11b that is surrounded by a bell mouth 12, are formed in a casing 11.
  • the intake port 11b faces the side plate 32 of the impeller 13.
  • the discharge port 11a is formed in a direction that is perpendicular to the intake port 11b so that air is blown out in a direction approximately perpendicular to a rotational axis O-O of the impeller 13.
  • the impeller 13 rotates in a rotational direction R (shown in Fig. 3 ) with respect to the casing 11. This allows each blade 33 of the impeller to scoop out air from the inner peripheral side of the impeller 13 to a space on the outer peripheral side thereof, draw in air from the intake port 11b into the inner peripheral space of the impeller 13, and blow the air that was pushed out to the outer peripheral side of the impeller 13 through the discharge port 11a.
  • the multi-blade fan 10 draws in air from the intake port 11b and blows air out from the discharge port 11a.
  • This type of multi-blade fan 10 produces turbulent vortices that causes noise to be produced near the main plate 31. More specifically, these turbulent vortices are generated by the mechanism described below.
  • air drawn into the interior of the impeller 13 from the intake port 11b mainly flows toward the main plate 31 and then gradually toward the outer periphery (see air flow W).
  • air flow W mainly flows toward the main plate 31 and then gradually toward the outer periphery
  • a portion of the air drawn in from the intake port 11b collides with the main plate 31, and then flows toward the outer peripheral side near the main plate 31 (see air flow X).
  • Turbulent vortices are generated in this air flow X due to the collision with the main plate 31.
  • the turbulent vortices flow in the air flow X toward the outer periphery and further merge with the air flow that collides with the main plate 31.
  • the turbulent vortices in the air flow X then gradually grow, and the biggest turbulent vortices are formed on the inner peripheral edges of the blades 33. These enlarged turbulent vortices are scooped out toward the outer periphery by the blades 33, and this generates noise.
  • swirling vortices are produced in this type of multi-blade fan 10 in which the centers thereof are near the outer peripheral edge of the side plate 32.
  • the swirling vortices do not assist the impeller 13 to blow air, and thus as a result, the swirling vortices cause noise and reduce fan efficiency. More specifically, the swirling vortices are generated by the mechanism described below.
  • the noise caused by turbulent vortices generated near the main plate is not limited to multi-blade fans, but is also produced in centrifugal fans that include a turbo fan and the like.
  • GB 1 140 688 A discloses a fan impeller of a centrifugal fan for handling dust laden gases.
  • the impeller in this document does not have jagged shaped wave form members formed on a main plate side of a side plate disposed on the outer peripheral side of the ends of the blades.
  • JP 58 059397 A and JP 56 054993 A Further prior art is also known from JP 58 059397 A and JP 56 054993 A .
  • an impeller of a centrifugal fan comprising: a main plate that rotates about a rotational axis; a plurality of blades that are annularly disposed about the rotational axis, one end of each of the plurality of blades fixed to the main plate; and an annular side plate that is disposed on the outer peripheral side of the other ends of the blades, and is connected to the other ends of the plurality of blades; wherein jagged shaped wave form members are formed on the main plate side of the side plate.
  • An advantage obtainable with embodiments of the present invention is to provide an impeller that is capable of reducing noise, and to provide a low noise centrifugal fan.
  • the impeller for a centrifugal fan disclosed in claim 2 is the impeller disclosed in claim 1, in which the wave form members are triangular wave forms.
  • the impeller for a centrifugal fan disclosed in claim 3 is the impeller disclosed in claim 1, in which the wave form members are sine wave forms.
  • the impeller for a centrifugal fan disclosed in claim 4 is the impeller disclosed in claim 1, in which the wave form members are rectangular wave forms.
  • the impeller for a centrifugal fan disclosed in claim 5 is the impeller disclosed in any of claims 1 to 4, in which the wave form members have wave pitches in a range between 2 mm and 8 mm and wave heights in a range between 1 mm and 5 mm.
  • the wave form members When these wave form members are provided on the side plate side of the main plate surface near the inner peripheral side of the blades, the wave form members will be better able to reduce noise causing turbulent vortices produced on the surface of the main plate on the side plate side near the inner peripheral side of the blades. In addition, when these wave form members are provided on the surface of the side plate on the main plate side, the wave form members will be better able to reduce swirling vortices near the side plate that cause an increase in the B F value.
  • the centrifugal fan disclosed in claim 6 includes the impeller set forth in any of claims 1 to 5, a drive means that rotates the main plate, and a casing that covers the impeller and which includes an intake port that faces an opening in an inner peripheral side of the side plate and a discharge port that is provided on an outer peripheral side of the impeller and which blows air in a direction approximately perpendicular to the rotational axis.
  • each blade of the impeller scoops out air from the inner peripheral side of the impeller to a space on the outer peripheral side thereof, draws in air from the intake port into the inner peripheral space of the impeller, and blows the air that was pushed out to the outer peripheral side of the impeller through the discharge port.
  • the centrifugal fan draws in air from the intake port and blows out air from the discharge port.
  • the swirling vortices produced near the side plate will be reduced by the wave form members formed on the side plate surface. This allows fan efficiency to improve and noise to be reduced because the B F value will be reduced and the portion of the impeller can effectively blow air will be enlarged.
  • a multi-blade fan (centrifugal fan) according to an embodiment of the present invention differs from the conventional multi-blade fan 10 shown in Figs. 1 to 3 in that the impeller 13 includes jagged shaped wave form members on the main plate 31 near the inner peripheral edges of the plurality of blades, jagged shaped wave form members on the main plate 31 side of the side plate 32, and a plurality of inter-blade cut-out portions 35 that have been cut out from the main plate 31 on the front side in the rotational direction of the blades 33.
  • Fig. 4 shows a lateral cross-sectional view of a multi-blade fan 40 of the present embodiment
  • Figs. 5 and 6 show a lateral cross-sectional view and a plan view of an impeller 43 of the multi-blade fan 40.
  • the multi-blade fan 40 is primarily composed of an impeller 63, a casing 11 that covers the impeller 63, and a motor 14 that rotates the impeller 43.
  • the impeller 43 includes a disk-shaped main plate 61 to which a plurality of blades 33 are fixed to the outer peripheral edge thereof, and an annular side plate 62 to which the other ends of the plurality of blades 33 are connected. A detailed description of the impeller 43 will be provided below.
  • the intake port 11b faces the side plate 62 of the impeller 43. Air that flows through the intake port 11b and into the space in the interior of the impeller 43 generally flows along the rotational axis O-O of the impeller 43 when it enters this space, and then flows in a direction away from the rotational axis O-O (toward the outer periphery of the impeller 43) due to the rotation of the impeller 43.
  • the discharge port 11a is formed such that it is perpendicular to the intake port 11b, so that air is blown out in a direction approximately perpendicular to the rotational axis O-O of the impeller 43.
  • a rotation shaft of the motor 14 is mounted in a central hole 61a in the main plate 61 (see Fig. 6 ), and rotates the impeller 43 by rotating the main plate 61.
  • the main portion of the motor 14 is fixed to the casing 11.
  • the impeller 43 will now be described.
  • the impeller 43 includes the main plate 61, the plurality of blades 33, and the annular side plate 62.
  • the impeller 43 is a product made of a synthetic resin in which a mold is used to unitarily form the main plate 61, the plurality of blades 33, and the side plate 62 together.
  • the main plate 61 is a disk-shaped member in which the central hole 61 a is formed, and the rotation shaft of the motor 14 is fixed in the central hole 61 a.
  • the plurality of blades 33 are formed around the outer peripheral edge of the main plate 61 and are equidistant with respect to each other in the rotational direction.
  • Jagged shaped wave form members 64 are formed around a circumference of the main plate 61 near the inner peripheral edges of the plurality of blades 33.
  • the wave form members 64 include triangular wave forms that have a wave pitch P of 3 mm and a wave height H of 2 mm (see Fig. 7(a) ).
  • the wave form members are not limited to triangular wave forms, and as shown in Figs. 7(b) and 7(c) , may have wave forms shaped like sine waves or rectangles.
  • the dimensions of the wave form members are not limited to those of the present embodiment, and the wave pitch P may be in a range between 2 mm and 8 mm, and the wave height H may be in a range between 1 mm and 5 mm.
  • inter-blade portions 65 located between the plurality of blades 33 are cut out from the main plate 61 on the front sides in the rotational direction of the plurality of blades 33.
  • the plurality of inter-blade portions 65 are larger in the circumferential direction than the thickness in the circumferential direction of the blades 33, and are cut out on the front side in the rotational direction of the blade 33 with a length that does not reach the rear side in the rotational direction of the adjacent other blades 33.
  • the inter-blade portions 65 are cut out in the radial direction along the shape of the blades 33 at a length that extends from the outer peripheral edge of the blades 33 to the inner peripheral edge of the blades 33.
  • the blades 33 include a recessed surface on the front sides thereof in the rotational direction, and these members are annularly disposed with the rotational axis O-O at the center thereof.
  • One end of the blades 33 are fixed to the outer peripheral edge of the main plate 61, and extend lengthwise from this point along the rotational axis O-O without twisting. Then, as shown in Figs. 5 and 6 , the other end of the blades 33 are connected to the annular side plate 62.
  • the annular side plate 62 is disposed on the outer peripheral side of the other ends of the blades 33, and is connected to each blade 33.
  • the side plate 62 is unitarily formed together with the main plate 61 and the plurality of blades 33.
  • the jagged shaped wave form members 66 are formed on the main plate 61 side of the side plate 62.
  • the wave form members 66 includes triangular wave forms that have a wave pitch P of 3 mm and a wave height H of 2 mm (see Fig. 7(a) ).
  • the wave form members are not limited to triangular wave forms, and as shown in Figs. 7(b) and 7(c) , may have wave forms shaped like sine waves or rectangles.
  • the dimensions of the wave form members are not limited to those of the present embodiment, and the wave pitch P may be in a range between 2 mm and 8 mm, and the wave height H may be in a range between 1 mm and 5 mm.
  • the impeller 43 rotates in a rotational direction R (shown in Fig. 6 ) with respect to the casing 11.
  • air will be scooped out primarily by the recessed surface on the front side in the rotational direction of the blades 33 of the multi-blade fan 40.
  • This allows the blades 33 of the impeller 43 to scoop out air from the inner peripheral side of the impeller 43 to a space on the outer peripheral side thereof, draw in air from the intake port 11b into the inner peripheral space of the impeller 43, and accumulate and blow the air that was scooped out to the outer peripheral side of the impeller 43 and out the discharge port 11a (see air flow Z in Fig. 4 ).
  • the multi-blade fan 40 draws in air from the intake port 11b along the rotational axis O-O, and the air is then blown out from the discharge port 11a in a direction that is perpendicular to the rotational axis O-O. Note that although only the air flow Z on the right side of the rotational shaft O-O is shown in Fig. 4 , the air scooped out to the outer peripheral side of the impeller 13 on the left side of the rotational axis O-O will flow along the casing 11 to the discharge port 11a and then be blown out.
  • the inter-blade portions 65 on the main plate 61 of the impeller 43 of the present embodiment are larger in the circumferential direction that the thickness in the circumferential direction of the blades 33, and the inter-blade portions 65 are cut out to a length that extend from the outer peripheral edge of the blades 33 to the inner peripheral edges of the blades 33 along the curved shape of the blades 33.
  • the inter-blade portions 65 are used to stack two impellers 43 along the rotational axis O-O.
  • the blades 33 on one impeller 43 can be fit into the corresponding plurality of inter-blade portions 65 on another impeller 43. Two impellers 43 fit together in this way can be stacked together to a predetermined height and then transported.
  • the present experiment is one in which sound measurements were taken from the conventional example shown in Figs. 2 and 3 and the present embodiment shown in Figs. 5 and 6 .
  • the wave form members 64 formed on the main plate 61, the wave form members 66 formed on the side plate 62, and the inter-blade portions 65 on the main plate 61 are simultaneously formed in order to reduce noise. Accordingly, in order to confirm the sound reduction effects of these three elements, impellers having only one of each of these three elements were prepared and a sound reduction experiment was conducted on each impeller. The results of these sound reduction experiments are shown below.
  • the special characteristics of the multi-blade fan of the present embodiment are as follows.
  • noise is produced by turbulent vortices generated near the main plate 31. More specifically, the turbulent vortices are generated by the mechanism described below.
  • a portion of the air drawn in from the intake port 11b collides with the main plate 31 in the interior of the impeller 13, and then flows near the main plate 31 toward the outer peripheral side (see air flow X).
  • Turbulent vortices are generated in this air flow X due to the collision with the main plate 31.
  • the turbulent vortices flow with the air flow X toward the outer periphery and further merge with the air flow that collides with the main plate 31.
  • the turbulent vortices in the air flow X then gradually grow, and the biggest turbulent vortices are formed on the inner peripheral edges of the blades 33. These enlarged turbulent vortices are scooped out toward the outer periphery by the blades 33, and this generates noise.
  • the turbulent vortices that grew due to the collision of the air flow Z1 with the main plate 61 and the merger with the air flow will be reduced in size immediately before reaching the blades 33 because the wave form members 64 are formed on at least the side plate 62 side of the main plate 61 near the inner peripheral edges of the blades 33. This allows the noise generated when the air flow Z1 is scooped out by the blades 33 to be reduced.
  • swirling vortices are produced in which the centers thereof are near the outer peripheral edge of the side plate 32.
  • the swirling vortices do not assist the impeller 13 to blow air, and thus as a result, the swirling vortices cause noise and reduce fan efficiency. More specifically, the turbulent vortices are generated by the mechanism described below.
  • a portion of the air inside the casing 11 is scooped out to the outer periphery of the impeller 13, and then swirling vortices Y are produced near the side plate 32 such that air is again drawn in from near the bell mouth 12 of the impeller 13 to the inner peripheral side of the impeller 13. Because of this, a portion of the air cannot be effectively blown, and this portion corresponds to a ratio b/B (hereinafter referred to as blockage factor B F ) between a length b in the axial direction of the portion of the impeller 13 that produces the swirling vortices Y and a length B in the axial direction of the entire impeller 13. Because of this, there will be a reduction in fan efficiency and noise will be generated.
  • the pressure fluctuations near the impeller 43 exit of the side plate 62 will be reduced because the wave form members 66 are formed on the main plate 61 side of the side plate 62 surface.
  • inter-blade portions 65 of the impeller 43 of the present embodiment are partially cut out from the front side in the rotational direction of the main plate 61, and are not cut out up to the rear side in the rotational direction of the inter-blade portions 65.
  • the inter-blade portions 65 of the impeller 43 of the present embodiment are partially cut out from the front side in the rotational direction of the main plate 61, and are not cut out up to the rear side in the rotational direction of the inter-blade portions 65.
  • the turbulent vortices of the air flow Z3 easily escape from the cut-out inter-blade portions 65 before they arrive at the outer peripheral edges of the blades 33 because the inter-blade portions 65 of the impeller 43 of the present embodiment are cut out from the outer peripheral edges of the blades 33 to the inner peripheral edges thereof. In this way, the turbulent vortices that arrive at the outer peripheral edges of the blades 33 can be further diminished, and noise can be further reduced.
  • the inter-blade portions 65 of the main plate 61 of the impeller 43 of the present embodiment are larger in the circumferential direction that the thickness in the circumferential direction of the blades 33, and the inter-blade portions 65 are cut out to a length that extends from the outer peripheral edges of the blades 33 to the inner peripheral edges of the blades 33 along the curved shape of the blades 33.
  • This shape is used to stack two impellers 43 from the rotational axis O-O, and the blades 33 can be respectively fit into the cut-outs of the plurality of inter-blade portions 65. In this way, the load efficiency when loading the impellers 43 can be improved.
  • the present invention is applied to impellers for turbo fans.
  • the wave form members 64 formed on the main plate 61 of the multi-blade fan 40 of the aforementioned embodiment is applied to an impeller 73 of a turbo fan.
  • Fig. 9 shows a cross-sectional plan view of the impeller 73 of the turbo fan of the present embodiment.
  • the impeller 73 includes a disk-shaped main plate 91 to which a plurality of blades 93 are fixed to the outer peripheral edge thereof, and an annular shroud (side plate) not shown in the figures to which the other ends of the plurality of blades 93 are connected.
  • the plurality of blades 93 are formed around the outer peripheral edge of the main plate 91 and are equidistant with respect to each other in the rotational direction.
  • Jagged shaped wave form members 94 are formed around a circumference of the main plate 91 near the inner peripheral edges of the plurality of blades 93.
  • the wave form members 94 include the triangular waves, sine waves or rectangles shown in Figs. 7(a) - 7(c) that have a wave pitch P between 2 mm and 8 mm and a wave height H between 1 mm and 5 mm.
  • the wave form members 94 are formed at least on the shroud side of the main plate 91 near the inner peripheral edges of the blades 93, turbulent vortices that grew due to the collision of the air flow with the main plate 91 and the merger with the air flow will be reduced in size immediately before reaching the blades 93, and noise generated when the air flow is scooped out by the blades 93 can be reduced.
  • the present invention was applied to a centrifugal fan that employs an impeller made of a synthetic resin.
  • the present invention can be applied to a centrifugal fan that employs an impeller made of sheet metal.

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

Claims (6)

  1. Impulseur (43) d'un ventilateur centrifuge, comprenant :
    une plaque principale (61) qui tourne autour d'un axe de rotation (O-O) ;
    une pluralité d'ailettes (33) qui sont disposées annulairement autour de l'axe de rotation (O-O), une extrémité de chacune de la pluralité d'ailettes (33) étant fixée à la plaque principale (61, 91), et
    une plaque latérale (62) annulaire qui est disposée sur le côté périphérique extérieur des autres extrémités des ailettes (33), et est reliée aux autres extrémités de la pluralité d'ailettes (33),
    dans lequel des éléments en forme d'onde dentelés (66) sont formés sur le côté de plaque principale (61) de la plaque latérale (62).
  2. Impulseur (43, 73) pour un ventilateur centrifuge tel que revendiqué dans la revendication 1, dans lequel les éléments en forme d'onde (64, 66, 94) comprennent des formes d'ondes triangulaires.
  3. Impulseur (43, 73) pour un ventilateur centrifuge tel que revendiqué dans la revendication 1, dans lequel les éléments en forme d'onde (64, 66, 94) comportent des formes d'ondes sinusoïdales.
  4. Impulseur (43, 73) pour un ventilateur centrifuge tel que revendiqué dans la revendication 1, dans lequel les éléments en forme d'onde (64, 66, 94) comportent des formes d'ondes rectangulaires.
  5. Impulseur (43, 73) pour un ventilateur centrifuge tel que revendiqué dans l'une quelconque des revendications 1 à 4, dans lequel les éléments en forme d'onde (64, 66, 94) ont des pas d'ondes dans une plage qui varie entre 2mm et 8mm et des hauteurs d'ondes dans une plage qui varie entre 1mm et 5mm.
  6. Ventilateur centrifuge, comprenant :
    l'impulseur (43, 73) tel que revendiqué dans l'une des revendications 1 à 5 ;
    un moyen d'entraînement (14) qui fait tourner la plaque principale (61, 91) ; et
    un boîtier (11) qui couvre l'impulseur (43, 73), et comporte un orifice d'admission (11b) qui regarde une ouverture dans un côté périphérique intérieur de la plaque latérale (62) et un orifice de décharge (11a) qui est prévu sur un côté périphérique extérieur de l'impulseur (43, 73) et qui souffle de l'air dans une direction sensiblement perpendiculaire à l'axe de rotation (O-O).
EP02738677A 2001-06-28 2002-06-12 Impulseur pour soufflante centrifuge et soufflante centrifuge dotee dudit impulseur Expired - Lifetime EP1411248B8 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2001196177 2001-06-28
JP2001196177A JP2003013885A (ja) 2001-06-28 2001-06-28 遠心送風機の羽根車及びそれを備えた遠心送風機
JP2001196178A JP4736252B2 (ja) 2001-06-28 2001-06-28 多翼送風機の羽根車及びそれを備えた多翼送風機
JP2001196178 2001-06-28
PCT/JP2002/005882 WO2003002873A1 (fr) 2001-06-28 2002-06-12 Impulseur pour soufflante centrifuge et soufflante centrifuge dotee dudit impulseur

Publications (4)

Publication Number Publication Date
EP1411248A1 EP1411248A1 (fr) 2004-04-21
EP1411248A4 EP1411248A4 (fr) 2010-03-31
EP1411248B1 true EP1411248B1 (fr) 2012-05-02
EP1411248B8 EP1411248B8 (fr) 2012-06-20

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EP02738677A Expired - Lifetime EP1411248B8 (fr) 2001-06-28 2002-06-12 Impulseur pour soufflante centrifuge et soufflante centrifuge dotee dudit impulseur

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Country Link
EP (1) EP1411248B8 (fr)
CN (2) CN1212479C (fr)
AT (1) ATE556226T1 (fr)
ES (1) ES2387063T3 (fr)
WO (1) WO2003002873A1 (fr)

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DE202010018509U1 (de) 2010-02-26 2017-03-15 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
JP5287772B2 (ja) * 2010-03-16 2013-09-11 株式会社デンソー 遠心式多翼ファン
CN103216452B (zh) * 2013-04-25 2016-05-11 常州雷利电机科技有限公司 排水泵
ITCO20130069A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Compressore centrifugo multistadio
CN105298907A (zh) * 2014-06-19 2016-02-03 杨博胜 流体泵浦低紊流动叶轮
CN105020176A (zh) * 2015-08-20 2015-11-04 珠海格力电器股份有限公司 风叶、离心通风机
CN107328084B (zh) * 2017-07-31 2024-01-23 广东美的制冷设备有限公司 空调器的电机支架和空调器

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JPS5654993A (en) * 1979-10-11 1981-05-15 Hitachi Ltd Centrifugal impeller
JPS5859397A (ja) * 1981-10-02 1983-04-08 Hitachi Ltd 遠心形送風機
JPH0239595U (fr) * 1988-09-06 1990-03-16
JPH0239593U (fr) * 1988-09-06 1990-03-16
JP3191516B2 (ja) * 1993-08-25 2001-07-23 松下電器産業株式会社 電動送風機のインペラ

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CN1212479C (zh) 2005-07-27
ATE556226T1 (de) 2012-05-15
ES2387063T3 (es) 2012-09-12
EP1411248A4 (fr) 2010-03-31
WO2003002873A1 (fr) 2003-01-09
CN2575343Y (zh) 2003-09-24
CN1395045A (zh) 2003-02-05
EP1411248B8 (fr) 2012-06-20
EP1411248A1 (fr) 2004-04-21

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