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EP1933039A1 - Zentrifugallüfter und diesen einsetzende klimaanlage - Google Patents

Zentrifugallüfter und diesen einsetzende klimaanlage Download PDF

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Publication number
EP1933039A1
EP1933039A1 EP06810500A EP06810500A EP1933039A1 EP 1933039 A1 EP1933039 A1 EP 1933039A1 EP 06810500 A EP06810500 A EP 06810500A EP 06810500 A EP06810500 A EP 06810500A EP 1933039 A1 EP1933039 A1 EP 1933039A1
Authority
EP
European Patent Office
Prior art keywords
shroud
air
bellmouth
fan
centrifugal fan
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06810500A
Other languages
English (en)
French (fr)
Other versions
EP1933039A4 (de
Inventor
Zhiming Zheng
Tadashi Ohnishi
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
Original Assignee
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
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1933039A1 publication Critical patent/EP1933039A1/de
Publication of EP1933039A4 publication Critical patent/EP1933039A4/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers

Definitions

  • the present invention relates to a centrifugal fan and an air conditioner using the same, in particular to a technology to reduce noise of the centrifugal fan and air conditioner using the same.
  • centrifugal fan has been frequently employed for an air conditioner because it is highly efficient and low in noise level.
  • a ceiling built-in type air conditioner has been frequently utilized in recent years for commercial use, and a wall type air conditioner has been frequently utilized in households.
  • a heat exchanger is disposed at the blow-out side of a centrifugal fan to reduce the size.
  • a separated flow is brought about in the vicinity of the fan blow-out port on the surface of the shroud facing the main plate.
  • the separated flow generates noise, and at the same time, the air velocity distribution of air streams at the fan blow-out port is biased with respect to the main plate.
  • the air velocity distribution is made uneven in the heat exchanger, resulting from the air velocity distribution of air streams at the fan blow-out port being biased with respect to the main plate. This lowers the heat exchange efficiency of the heat exchanger, and increases the airflow resistance of the heat exchanger. As a result, power required to rotate the fan is accordingly increased, and at the same time, the energy efficiency is lowered.
  • Fig. 10 is a perspective view showing the appearance of impellers of a turbo fan as a prior art centrifugal fan
  • Fig. 11 is a longitudinal cross-sectional view showing a part of the same turbo fan.
  • the turbo fan includes a hub 101 that fixes the rotary shaft of a motor, a main plate 102 integrally formed on the outer circumference of the hub 101, a shroud 104 opposed to the main plate 102, which forms an air passage 103, a plurality of impellers 105 disposed between the main plate 102 and the shroud 104, and a bellmouth 106 disposed at the suction side of the shroud 104.
  • the hub 101, main plate 102, shroud 104 and impellers 105 compose an impeller wheel of the turbo fan.
  • the impeller wheel rotates in the direction of arrow R shown in Fig. 10 .
  • the bellmouth 106 is attached to a member, for example, a casing, which composes an air conditioner in which the turbo fan is used.
  • a fan suction port 107 is formed at the central part of the bellmouth 106, and the portion corresponding to the outer circumference of the shroud 104 in the air passage 103 composes a fan blow-out port 108.
  • a part of air streams blown out from the fan blow-out port 108 is brought in the suction port 104a of the shroud 104 along the surface of the bellmouth 106.
  • the part of the air streams forms circulation air streams that are drawn in the impellers of the turbo fan through clearance 109 between the bellmouth 106 and the shroud 104, and are blown out again through the blow-out port 108 of the fan. Since a change in shape of the surface 104b of the shroud 104 facing the main plate 102 from the suction port 104a to the fan blow-out port 108 is radical, a separate flow E is formed in the vicinity of the fan blow-out port 108. Therefore, there is a problem that noise occurs due to the separated flow E as described above, and the air velocity distribution at the fan blow-out port 108 is biased with respect to the main plate 102.
  • a turbo fan described in Patent Document 1 has been proposed.
  • the basic construction of the turbo fan is the same as that of the turbo fan shown in Figs. 10 and 11 .
  • the shape of the impellers is devised as described below. That is, in the impellers of the turbo fan described in Patent Document 1, the position of the coupling portion with the shroud at the rear edge part is offset from the coupling portion with the main plate by a predetermined amount in a direction opposite to the rotation direction.
  • the positive pressure surface of the shroud side blade element is formed to protrude, and at the same time, the maximum warping position of the camber line of the shroud side blade element is located at the front edge part from the intermediate position of the chord length.
  • the impeller inlet angle at the shroud side is formed to be at the same angle as that in the case where the camber line of the shroud side blade element is made into a simple arc camber line. Also, the camber line of the main plate side blade element has a simple arcuate shape. Therefore, the impeller outlet angle at the shroud side becomes large, wherein the impeller outlet angle at the shroud side is closer to the impeller outlet angle at the main plate side.
  • the turbo fan according to Patent Document 1 is constructed as described above, so that the separated flow is suppressed by applying a force in the shroud direction to air streams that are flown from the front edge part of the impellers and flow toward the rear edge part of the impellers.
  • the turbo fan is designed to make uniform the air velocity distribution in the height direction of impellers at the fan blow-out port by making the impeller outlet angle at the shroud side closer to the impeller outlet angle at the main plate side.
  • Patent Document 1 Japanese Laid-Open Patent Publication No. 5-312189
  • the turbo fan according to Patent Document 1 cannot sufficiently prevent separated flows generated in the vicinity of the fan blow-out port on the surface of the shroud facing the main plate. For this reason, noise resulting from the separated flows cannot be sufficiently prevented from occurring. Also, the air velocity distribution in the height direction of the impellers at the fan blow-out port is biased to the main plate. Further, in an air conditioner having a turbo fan according to Patent Document 1 mounted therein, there is still a problem in that running noise in the air conditioner employing the turbo fan according to Patent Document 1 is still great. In an air conditioner in which a turbo fan according to Patent Document 1 is used and at the same time, a heat exchanger is disposed at the fan blow-out side, the air velocity distribution becomes uneven in the heat exchanger.
  • centrifugal fan having a novel construction applicable to general air conditioners, which centrifugal fan is capable of making uniform air velocity distribution in the height direction of the impellers at the blow-out port of the centrifugal fan by suppressing separated flows generated in the vicinity of the fan blow-out port on the surface of a shroud facing the main plate, and capable of reducing running noise of the centrifugal fan. Also, it is another objective of the present invention to provide an air conditioner capable of reducing running noise by using a thus constructed centrifugal fan, in an air conditioner having a centrifugal fan mounted therein.
  • a centrifugal fan which includes a hub for fixing a rotary shaft of a motor, a main plate formed at an outer circumference of the hub, a shroud opposed to the main plate, which forms air passages, a plurality of impellers disposed between the main plate and the shroud, and a bellmouth disposed at the suction side of the shroud.
  • a plurality of projections or recesses, which form air streams from a center of the shroud toward an outer circumference of the shroud along the surface of the shroud when running the fan, are formed on the surface of the shroud facing the bellmouth.
  • air streams flowing from the center of the shroud toward the outer circumference thereof along the surface are created by the projections or recesses formed on the surface of the shroud facing the bellmouth.
  • the air streams are developed to circulation streams from outer circumference of the shroud to the center of the shroud via the surface of the outer circumferential wall of the bellmouth, and then from the center of the shroud to the outer circumference of the shroud. Therefore, a part of air streams blown out from the fan blow-out port is drawn in and circulated by the circulation streams.
  • a plurality of rib-shaped projections which form air streams from the center of the shroud toward the outer circumference of the shroud along the surface when running the fan are formed on the surface of the shroud facing the bellmouth.
  • the rib-shaped projections on the surface of the shroud facing the bellmouth have substantially the same inclination as that of the camber line of the shroud side blade element of the impellers, and at the same time, the rib-shaped projections are formed at even intervals on the entire circumference of the surface of the shroud facing the bellmouth.
  • the amount of air that is drawn in from air streams blown out from the fan blow-out port by circulation air streams on the surface of the shroud facing the bellmouth is increased.
  • the air streams from the suction port of the shroud toward the fan blow-out port along the surface of the shroud facing the main plate are increased, and separated flows is prevented from occurring in the vicinity of the fan blow-out port on the surface of the shroud facing the main plate.
  • the pitch of rib-shaped projections on the surface of the shroud facing the bellmouth is smaller than the pitch of the impellers.
  • the height of the rib-shaped projections on the surface of the shroud facing the bellmouth is equivalent to the thickness of a plate that forms the shroud. According to the construction, when the shroud is integrally molded of resin, the amount of fluctuation in the thickness in the entirety of the shroud is reduced, and molding of the shroud is facilitated. In addition, the rib-shaped projections of the shroud have appropriate height with respect to small spacing formed between the shroud and the bellmouth. As a result, it is possible to efficiently generate the circulation streams and to efficiently reduce noise.
  • the rib-shaped projection of the shroud facing the bellmouth has a front side vertically extending from the surface of the shroud facing the bellmouth and positioned forward in the rotation direction of the impellers, a rear side vertically extending from the surface of the shroud facing the bellmouth and at the same time, positioned rearward in the rotation direction of the impellers, and a distal end face for connecting both sides together.
  • the distal end face is connected to the front side so that they are substantially orthogonal to each other, and the rear side is curved to the front side toward the distal end.
  • the front side that functions as the positive pressure side vertically extends to the distal end, it is possible to maintain the generation capacity of air streams advancing from the center of the surface of the shroud facing the bellmouth toward the outer circumference thereof at a high level.
  • the rear side that functions as the negative pressure side is curved to the front side toward the distal end, air is easily brought in the negative pressure side, and it is possible to prevent eddies from occurring at the negative pressure side. Resultantly, air streams from the center on the surface of the shroud facing the bellmouth toward the outer circumference are further efficiently generated, and it is possible to prevent noise from occurring due to eddies at the negative pressure side.
  • Another aspect of the present invention provides an air conditioner having the above-described centrifugal fan mounted therein. With such a construction, noise of the air conditioner is reduced since the running noise of the centrifugal fan is reduced.
  • an air suction port for drawing in indoor air is formed at the front side of the fan suction port of the centrifugal fan.
  • a heat exchanger is disposed at the blow-out side of the centrifugal fan.
  • An air blow-out port for blowing air indoors is disposed downstream of the heat exchanger.
  • the centrifugal fan is a turbo fan. With such a construction, the fan efficiency is improved. At the same time, the running noise is further suppressed.
  • An air conditioner according to the present embodiment is an indoor unit for a wall type air conditioner, and has a laterally long box shape as shown in the perspective view of Fig. 1 .
  • the indoor unit is formed, as shown in the plan cross-sectional view of Fig. 2 , so that the thickness direction (the vertical direction in Fig. 2 ) becomes smaller.
  • a turbo fan 2 operating as an indoor fan and heat exchangers 4 for cooling or heating indoor air are accommodated in a main body casing 1.
  • the main body casing 1 is provided with a front plate 11 at the front side of the main body casing 1 as shown in the perspective view of Fig. 1 .
  • the front plate 11 is provided with an air suction port 12 for drawing in air at the middle part thereof, and is provided with air blow-out ports 13 for blowing out air which has been subjected to heat exchange by the heat exchangers 4.
  • a turbo fan 2 is disposed at the middle part in the interior of the main body casing 1, and the heat exchangers 4 are disposed at both sides.
  • the turbo fan 2 is disposed so that air drawn in through the air suction port 12 is blown out sideways of the turbo fan 2.
  • Each heat exchanger 4 is disposed at a blow-out side of the turbo fan 2.
  • An air passage 14 is formed in the main body casing 1 so that air drawn in by the turbo fan 2 is blown out indoors through the air blow-out ports 13 after being subjected to heat-exchange by the heat exchangers 4.
  • the turbo fan 2 includes an impeller wheel 21, a bellmouth 22 for guiding air into the impeller wheel 21, and a motor 23 for driving the impeller wheel 21 as shown in Fig. 2 .
  • the rotary shaft of the impeller wheel 21, that is, the rotary shaft 23a of the motor 23 is disposed at the middle part in the main body casing 1 so as to extend in the thickness direction of the main body casing 1.
  • the bellmouth 22 is disposed at the position corresponding to the air suction port 12.
  • a low-profile motor for example, a print motor is used as the motor 23, which is fixed at the position corresponding to the impeller wheel 21 on the backside of the main body casing 1.
  • the impeller wheel 21 is composed, as shown in Figs. 2 to 6 , of a hub 24 for fixing the rotary shaft 23a of the motor 23, a main plate 25 integrally formed on the outer circumference of the hub 24, a shroud 27 that is opposed to the main plate 25 and forms an air passage 26, and six impellers 28 that are disposed between the main plate 25 and the shroud 27.
  • Fig. 4 is a perspective view showing the appearance of the impeller wheel 21.
  • Fig. 5 is a enlarged perspective view showing the appearance of a part of the impeller wheel
  • Fig. 6 is a longitudinal cross-sectional view showing a part of the turbo fan 2. Arrows R shown in Figs. 3 to 5 , 7 and 8 described below show the rotation direction of the impeller wheel 21.
  • a fan suction port 29 is formed at the middle part of the bellmouth 22.
  • the bellmouth 22 functions as a partitioning wall that sections the suction side of the heat exchanger 4, cooperating with the front plate 11, as shown in Fig. 2 .
  • the part corresponding to the outer circumference of the shroud 27 in the air passage 26, that is, the rear edge part of the impellers 28 composes a fan blow-out port 30.
  • the construction of the impellers 28 is similar to that of the impellers described in Patent Document 1 described above. That is, at the impeller 28, the position of the coupling portion with the shroud 27 at the rear edge part thereof is offset by a predetermined amount in a direction opposite to the rotation direction from the position of the coupling portion with the main plate 25. Also, the positive pressure side of the shroud side blade element is formed to project, and the maximum warping position of the camber line of the shroud side blade element is positioned closer to the front edge than an intermediate position of the chord length. Furthermore, the impeller inlet angle at the shroud side is formed to be the same as that in the case where the camber line of the shroud side blade element is made into a simple arc camber line. At the same time, the camber line of the main plate side blade element has a simple arc shape.
  • a plurality of rib-shaped projections 31 that form air streams from the center of the shroud 27 toward the outer circumference thereof along the surface 27a when running the fan are formed on the surface 27a of the shroud 27 facing the bellmouth 22.
  • These rib-shaped projections 31 are formed so as to have substantially the same inclination as the camber line of the shroud side blade element of the impellers 28, and are formed at even intervals on the entire circumference of the surface 27a of the shroud 27.
  • the pitch of the rib-shaped projections 31 is formed to be small at approximately one-tenth of the pitch of the respective impellers 28.
  • each rib-shaped projection 31 includes a front side 32 located forward of the rotation direction of the impellers 21, a rear side 33 located rearward thereof, and a distal end face 34 that connects the front side 32 and the rear side 33 to each other.
  • the respective sides 32 and 33 vertically extend from the surface 27a of the shroud 27.
  • the front side 32 and the distal end face 34 are coupled so as to be orthogonal to each other.
  • the rear side 33 is curved to the front side 32 toward the distal end.
  • the heat exchangers 4 are separated and disposed substantially symmetrically with respect to the turbo fan 2 as shown in Fig. 2 . As shown in the perspective view of Fig. 9 , both heat exchangers 4 thus separated and disposed are connected to each other by refrigerant pipes 41 disposed in the space at the bottom of the main body casing 1, and are composed so as to operate integrally with each other. As shown in Fig. 9 , in each heat exchanger 4, six rows of flat tubes 44 are disposed between the front plate 42 and the rear plate 43 so that they extend in the thickness direction of the main body casing 1 and are disposed parallel to each other. Corrugated fins 45 intervene between these flat tubes 44, and between the flat tubes 44 and the front plate 42 or the rear plate 43. The flat tubes 44 and corrugated fins 45 are connected to each other by, for example, brazing.
  • the air conditioner constructed as described above and the turbo fan mounted in the air conditioner operate as follows. As operation of the air conditioner is commenced, and the turbo fan 2 is also run, indoor air is drawn in through the air suction port 12. The indoor air is taken from the fan suction port 29 and is brought into the air passage 26 of the turbo fan 2, and is then blown out from the fan blow-out port 30 by the pressure thereof increased by the impellers 28. Air blown out from the fan blow-out port 30 is subjected to heat exchange by respective heat exchangers 4, and is blown out indoors through the air blow-out ports 13.
  • the rib-shaped projections 31 formed on the surface 27a of the shroud 27 operate like impellers in the turbo fan 2, and air stream S1 flowing from the center of the shroud 27 toward the outer circumference thereof along the surface 27a is created.
  • the air stream S1 is developed to a circulation air stream S2 from the outer circumference of the shroud 27 to the center of the shroud 27 via the surface of the outer circumferential wall of the bellmouth 22, and then from the center of the shroud 27 to the outer circumference of the shroud 27.
  • air stream S4 that is a part of the air stream S3 blown out from the fan blow-out port 30 is drawn in and circulated by the circulation air stream S2.
  • the air stream S4 that is a part of the thus circulating air flows from the clearance 35 between the hub 24 and the shroud 27 toward the fan blow-out port 30 along the surface 27b of the shroud 27 facing the main plate 25. Accordingly, an air stream S5 along the surface 27b of the shroud 27 is increased.
  • the rib-shaped projections 31 are formed so as to have substantially the same inclination as that of the camber line of the shroud side blade element of the impellers 28. Therefore, the air stream direction of air streams S1 flowing along the surface 27a of the shroud 27 on the outer circumferential portion of the shroud 27 is the same as the direction of the air streams S3 discharged from the fan blow-out port 30. Thus, since the direction of the air streams S1 is the same as the direction the air streams S3, the amount of the air streams S4 drawn in from the air streams S3 discharged from the fan blow-out port 30 by the circulation air streams S2 on the surface 27a of the shroud 27 is increased.
  • the rib-shaped projections 31 are formed so that the pitch thereof is made remarkably smaller than the pitch of the impellers 28. Accordingly, it is possible to efficiently generate circulation air streams S2 in small spacing between the surface 27a of the shroud 27 and the bellmouth 22.
  • the height of the rib-shaped projections 31 is made equivalent to the thickness of the plate that forms the shroud 27. For this reason, when the entirety of the shroud 27 is integrally made of resin, the fluctuation amount of the thickness at the entire shroud 27 can be made low, so that molding of the shroud 27 is facilitated.
  • the rib-shaped projection 31 has an appropriate height with respect to small spacing formed between the shroud 27 and the bellmouth 22, so that the above-described circulation air streams S2 is efficiently generated, and noise is efficiently reduced.
  • the front side 32 located at the positive pressure side vertically extends to the distal end face 34, it is possible to maintain a high generation performance of air streams S1 flowing from the center at the surface 27a of the shroud 27 toward the outer circumference thereof.
  • the distal end portion of the rear side 33 located at the negative pressure side is formed to be like a circular arc. Accordingly, air is further easily brought in the negative pressure side, so that it is possible to prevent eddies F from occurring at the negative pressure side.
  • air streams flowing from the center on the surface 27a of the shroud 27 toward the outer circumference are further efficiently generated, so that noise due to eddies occurring at the negative pressure side is suppressed.
  • the position of the coupling portion with the shroud 27 at the rear edge part of the impellers 28 is offset by a predetermined amount in the direction opposite to the rotation direction from the position of the coupling portion with the main plate 25 as in the turbo fan according to Patent document 1 described above. Accordingly, air streams flowing in from the front edge part of the impellers 28 and flowing to the rear edge part of the impellers 28 receive a force in the direction toward the shroud 27. The separated flows E are thus prevented based on this point.
  • the positive pressure side of the shroud side blade element is formed like a projection, and at the same time, the maximum warping position of the camber line of the shroud side blade element is located closer to the front edge than an intermediate position of the chord length.
  • the impeller inlet angle at the shroud side is formed at the same angle as in the case where the camber line of the shroud side impeller element is made into a simple arc camber line, and the camber line of the main plate side blade element has a simple arc shape. Therefore, the impeller outlet angle at the shroud side is increased, and the impeller outlet angle at the shroud side is drawn near the impeller outlet angle at the main plate side. With such a construction, the air velocity distribution in the height direction of the impellers 28 at the fan blow-out port 30 is made uniform.
  • An air conditioner according to the present embodiment reduces running noise as an air conditioner since the running noise of the turbo fan 2 is reduced.
  • the air conditioner includes an air suction port 12, which draws in indoor air, at the front side of the fan suction port 29 of the turbo fan 2.
  • the heat exchangers 4 are disposed at the blow-out sides of the turbo fan 2, and the air blow-out ports 13 that blow out air into indoors are disposed downstream of the heat exchanger 4. Accordingly, since the dimension of each heat exchanger 4 in the thickness direction of the main body casing 1 is reduced, the outer dimension of the air conditioner in its thickness direction is reduced.
  • the air velocity distribution in the height direction of the impellers at the fan blow-out port 30 of the turbo fan 2 is made uniform, so that the air velocity distribution of the heat exchangers 4 is improved.
  • the heat exchange efficiency of the heat exchangers 4 is improved, and at the same time, the resistance inside the air conditioner is reduced, so that the energy efficiency of the air conditioner is improved.
  • the turbo fan 2 is used as an indoor fan. For this reason, the fan efficiency is further improved than in cases where other centrifugal fans are used, and the running noise is further suppressed.
  • the present embodiment may be modified as follows.
  • a centrifugal fan according to the present invention may be applicable to a general centrifugal fan such as a turbo fan, a sirocco fan, a radial fan, etc.
  • an air conditioner having the centrifugal fan mounted therein is applicable to various types of air conditioners for household and commercial use.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
EP06810500.6A 2005-09-30 2006-09-25 Zentrifugallüfter und diesen einsetzende klimaanlage Withdrawn EP1933039A4 (de)

Applications Claiming Priority (2)

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JP2005289208A JP4017003B2 (ja) 2005-09-30 2005-09-30 遠心ファン及びこれを用いた空気調和機
PCT/JP2006/318932 WO2007040073A1 (ja) 2005-09-30 2006-09-25 遠心ファン及びこれを用いた空気調和機

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2218917A1 (de) 2009-02-12 2010-08-18 ebm-papst Mulfingen GmbH & Co. KG Radial- oder Diagonal-Ventilatorrad
DE102010009566A1 (de) 2010-02-26 2011-09-01 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
WO2012062249A1 (de) * 2010-06-08 2012-05-18 Koppenwallner Georg E Verfahren zur beeinflussung des strömungsverhaltens von ungsmaschinen, insbesondere gebläse- oder absaugvorrichtungen sowie zugehörige gebläse- oder absaugvorrichtung
ITTO20110362A1 (it) * 2011-04-26 2012-10-27 Denso Corp Gruppo ventilatore per veicoli
DE202009018770U1 (de) 2009-02-12 2013-03-07 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
US10533577B2 (en) 2013-04-22 2020-01-14 Lennox Industries Inc. Fan systems
WO2022123484A1 (en) * 2020-12-10 2022-06-16 Innova S.R.L. Improved fan coil unit

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8347952B2 (en) * 2006-11-30 2013-01-08 Apple Inc. Enhanced vent for outlet for a cooling system
JP5293684B2 (ja) * 2010-06-03 2013-09-18 三菱電機株式会社 空気調和機の室内機
CN104981365B (zh) * 2013-02-12 2017-03-08 三菱电机株式会社 车辆用空调装置的室外冷却单元
CN103267319B (zh) * 2013-06-15 2015-12-30 邓明义 一种隐藏式空调器室内机
WO2015111210A1 (ja) * 2014-01-27 2015-07-30 三菱電機株式会社 遠心ファン及び空気調和装置
CN106457964B (zh) * 2014-06-11 2019-04-02 松下知识产权经营株式会社 温度调节单元、温度调节系统和具备温度调节单元的车辆
JP6369684B2 (ja) 2014-10-10 2018-08-08 株式会社富士通ゼネラル 天井埋込型空気調和機
KR101720491B1 (ko) * 2015-01-22 2017-03-28 엘지전자 주식회사 원심팬
CN104896588B (zh) * 2015-05-26 2018-03-30 广东美的制冷设备有限公司 空调室内机
CN107710495B (zh) * 2015-07-24 2020-12-01 松下知识产权经营株式会社 温度调节单元、温度调节系统、车辆
WO2018116340A1 (ja) * 2016-12-19 2018-06-28 三菱電機株式会社 空気調和装置
JP2018115585A (ja) * 2017-01-17 2018-07-26 日本電産コパル電子株式会社 送風機
CN107956746A (zh) * 2017-10-20 2018-04-24 珠海格力电器股份有限公司 一种用于离心风机的降噪集流器、离心风机和空调系统
ES2959400T3 (es) * 2017-12-13 2024-02-26 Mitsubishi Electric Corp Unidad de intercambio de calor y dispositivo de acondicionamiento de aire que tiene la misma montada en él
CN110454418B (zh) * 2018-05-07 2024-12-13 珠海格力电器股份有限公司 轴流风扇及具有其的空调器
JP7358280B2 (ja) * 2020-03-23 2023-10-10 三菱重工業株式会社 ダクテッドファン及び航空機
TWI724872B (zh) * 2020-04-17 2021-04-11 建準電機工業股份有限公司 離心扇輪及具有該離心扇輪的離心風扇
CN111845995A (zh) * 2020-08-28 2020-10-30 广东省智能制造研究所 一种低噪声负压爬壁机器人
CN112628199B (zh) * 2021-01-07 2022-05-24 泛仕达机电股份有限公司 一种减阻降噪的离心风轮
CN113915162B (zh) * 2021-11-05 2024-04-09 泛仕达机电股份有限公司 一种后向离心风机提效轮盘及后向离心风机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5186666U (de) * 1974-12-30 1976-07-12
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
US20050191174A1 (en) * 2004-02-27 2005-09-01 Ling-Zhong Zeng Centrifugal fan

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1879803A (en) * 1930-01-27 1932-09-27 Andrew G Johnson Rotary pump
US2207317A (en) * 1938-08-05 1940-07-09 Glenn M Freeman Centrifugal pump
US2349731A (en) * 1942-03-20 1944-05-23 Ingersoll Rand Co Centrifugal pump
US3224078A (en) * 1963-09-30 1965-12-21 Ruth D Mayne Method of making a turbine type blower wheel
JPS504606A (de) * 1973-05-18 1975-01-18
JPS5332406A (en) * 1976-09-08 1978-03-27 Hitachi Ltd Vane wheel
JPS56118593A (en) * 1980-02-25 1981-09-17 Hitachi Ltd Blower
US4521154A (en) * 1982-01-13 1985-06-04 Corbett Reg D Centrifugal fans
US4664592A (en) * 1983-07-14 1987-05-12 Warman International Limited Centrifugal pump impeller configured to limit fluid recirculation
JPS61145899U (de) * 1985-03-01 1986-09-09
DE3627778A1 (de) * 1986-08-16 1988-02-18 Bbc Brown Boveri & Cie Beruehrungsfreie zentrifugaldichteinrichtung fuer einen rotierenden maschinenteil
AU595656B2 (en) * 1986-10-07 1990-04-05 Weir Warman Ltd Impeller
SU1528035A1 (ru) * 1987-02-18 1994-10-30 А.И. Золотарь Центробежный насос
JPH03100254A (ja) * 1989-09-11 1991-04-25 Sekisui Chem Co Ltd 軒樋
JP2809867B2 (ja) * 1990-11-14 1998-10-15 松下電器産業株式会社 電動送風機
AUPN143795A0 (en) * 1995-03-01 1995-03-23 Sykes Pumps Australia Pty Limited Centrifugal pump
US5855469A (en) * 1997-07-17 1999-01-05 Iowa State University Research Foundation, Inc. End seal design for blower
JP2001182692A (ja) * 1999-12-28 2001-07-06 Osaka Gas Co Ltd 遠心式送風機
JP2004060622A (ja) * 2002-07-31 2004-02-26 Daikin Ind Ltd シロッコ形遠心ファンロータを用いた遠心送風機および空気調和機
CN1784547B (zh) * 2003-05-01 2011-07-20 大金工业株式会社 多叶片离心式送风机
JP3698150B2 (ja) * 2003-05-09 2005-09-21 ダイキン工業株式会社 遠心送風機
AU2003903024A0 (en) * 2003-06-16 2003-07-03 Weir Warman Ltd Improved pump impeller
JP3100254U (ja) * 2003-09-04 2004-05-13 志合電脳股▼分▲有限公司 遠心スイングバック式放熱ファンの羽根構造

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5186666U (de) * 1974-12-30 1976-07-12
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
US20050191174A1 (en) * 2004-02-27 2005-09-01 Ling-Zhong Zeng Centrifugal fan

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2007040073A1 *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202009018770U1 (de) 2009-02-12 2013-03-07 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
EP2218917A1 (de) 2009-02-12 2010-08-18 ebm-papst Mulfingen GmbH & Co. KG Radial- oder Diagonal-Ventilatorrad
US8454317B2 (en) 2009-02-12 2013-06-04 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial or diagonal fan wheel
US8932019B2 (en) 2010-02-26 2015-01-13 Emb-Papst Mulfingen Gmbh & Co. Kg Radial or diagonal fan wheel
DE102010009566A9 (de) 2010-02-26 2012-03-01 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
EP2363609A1 (de) 2010-02-26 2011-09-07 ebm-papst Mulfingen GmbH & Co. KG Radial- oder Diagonal-Ventilatorrad
DE102010009566A1 (de) 2010-02-26 2011-09-01 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
DE202010018509U1 (de) 2010-02-26 2017-03-15 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonal-Ventilatorrad
WO2012062249A1 (de) * 2010-06-08 2012-05-18 Koppenwallner Georg E Verfahren zur beeinflussung des strömungsverhaltens von ungsmaschinen, insbesondere gebläse- oder absaugvorrichtungen sowie zugehörige gebläse- oder absaugvorrichtung
ITTO20110362A1 (it) * 2011-04-26 2012-10-27 Denso Corp Gruppo ventilatore per veicoli
EP2517916A1 (de) * 2011-04-26 2012-10-31 DENSO THERMAL SYSTEMS S.p.A. Gebläsevorrichtung fü Fahrzeuge
US9180772B2 (en) 2011-04-26 2015-11-10 Denso Thermal Systems S.P.A. Fan assembly for vehicles
US10533577B2 (en) 2013-04-22 2020-01-14 Lennox Industries Inc. Fan systems
WO2022123484A1 (en) * 2020-12-10 2022-06-16 Innova S.R.L. Improved fan coil unit

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JP4017003B2 (ja) 2007-12-05
CN101253333A (zh) 2008-08-27
WO2007040073A1 (ja) 2007-04-12
KR20080037722A (ko) 2008-04-30
US20090255654A1 (en) 2009-10-15
JP2007100548A (ja) 2007-04-19
AU2006298249A1 (en) 2007-04-12
CN100559032C (zh) 2009-11-11
AU2006298249B2 (en) 2010-02-18
KR100934556B1 (ko) 2009-12-29
EP1933039A4 (de) 2014-05-07

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