WO2007040073A1 - Ventilateur centrifuge et climatiseur associé - Google Patents

Ventilateur centrifuge et climatiseur associé Download PDF

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Publication number
WO2007040073A1
WO2007040073A1 PCT/JP2006/318932 JP2006318932W WO2007040073A1 WO 2007040073 A1 WO2007040073 A1 WO 2007040073A1 JP 2006318932 W JP2006318932 W JP 2006318932W WO 2007040073 A1 WO2007040073 A1 WO 2007040073A1
Authority
WO
WIPO (PCT)
Prior art keywords
shroud
centrifugal fan
fan
bell mouth
air
Prior art date
Application number
PCT/JP2006/318932
Other languages
English (en)
Japanese (ja)
Inventor
Zhiming Zheng
Tadashi Ohnishi
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.
Priority to EP06810500.6A priority Critical patent/EP1933039A4/fr
Priority to AU2006298249A priority patent/AU2006298249B2/en
Priority to KR1020087006553A priority patent/KR100934556B1/ko
Priority to US11/992,645 priority patent/US20090255654A1/en
Publication of WO2007040073A1 publication Critical patent/WO2007040073A1/fr

Links

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 centrifugal fan, and more particularly to noise reduction in a centrifugal fan and an air conditioner using the centrifugal fan.
  • centrifugal fans are frequently used in air conditioners because of their high efficiency and low noise.
  • ceiling-embedded air conditioners are often used in the commercial field, and wall-mounted air conditioners are often used in the household field.
  • a structure in which a heat exchanger is arranged on the outlet side of a centrifugal fan is becoming increasingly popular for downsizing.
  • FIG. 10 is a perspective view showing the external appearance of an impeller of a turbo fan as a conventional centrifugal fan
  • FIG. 11 is a longitudinal sectional view showing a part of the turbo fan.
  • the turbofan is a hub 101 that fixes the rotating shaft of the motor, a main plate 102 that is integrally formed on the outer periphery of the hub 101, and a gas flow path 103 that is disposed so as to face the main plate 102.
  • the shroud 104, main plate 102 and shroud 1 And a plurality of blades 105 disposed between the four and the bell mouth 106 disposed on the suction side of the shroud 104.
  • the hub 101, the main plate 102, the shroud 104, and the blade 105 constitute a turbofan impeller. This impeller rotates in the direction of arrow R shown in FIG.
  • the bell mouth 106 is attached to a member constituting an air conditioner using a turbo fan, for example, a casing.
  • a fan suction port 107 is formed at the center of the bell mouth 106, and a portion corresponding to the outer periphery of the shroud 104 in the air flow path 103 constitutes a fan outlet 108.
  • turbo fan described in Patent Document 1 has been proposed.
  • the basic structure of this turbofan is the same as the turbofan shown in Fig. 10 and Fig. 11, but the shape of the force blade is devised as follows. That is, in the turbofan blade described in Patent Document 1, the position force of the joint portion with the shroud at the rear edge is offset by a predetermined amount on the opposite side of the rotational direction from the position of the joint portion with the main plate. Further, the pressure surface of the shroud blade element is formed in a projecting shape, and the maximum warp position of the camber wire of the shroud blade element is located at the leading edge of the intermediate position of the chord length.
  • the shroud side blade inlet angle is formed at the same angle as when the camber wire of the shroud side blade blade element is a single arc chamber line, and the camber wire of the main plate side blade element has a single arc shape. Yes. As a result, the blade outlet angle on the shroud side is increased, and the blade outlet angle on the shroud side is close to the blade outlet angle on the main plate side.
  • the turbofan described in Patent Document 1 is configured such that the blades are configured as described above.
  • the leading edge force of the root is intended to suppress the separation flow by applying a force in the shroud direction to the air flow that flows in and flows toward the trailing edge of the blade.
  • the turbofan achieves a uniform wind speed distribution in the height direction of the blades at the fan outlet by bringing the blade outlet angle on the shroud side closer to the blade outlet angle on the main plate side.
  • Patent Document 1 JP-A-5-312189
  • the turbofan described in Patent Document 1 also requires further improvement in the wind speed distribution in the height direction of the blades at the fan outlet. Moreover, since the wings of the turbo fan described in Patent Document 1 have a special shape, they cannot be applied to a general air conditioner centrifugal fan. Therefore, an improvement measure applicable to a centrifugal fan of a general air conditioner has been demanded.
  • a hub for fixing the rotating shaft of the motor a main plate formed on the outer periphery of the hub, a shroud disposed opposite to the main plate to form a gas flow path, and between the main plate and the shroud
  • a centrifugal fan having a plurality of blades disposed on the inlet and a bell mouth disposed on the suction side of the shroud.
  • the surface of the shroud with respect to the bell mouth is formed with a plurality of protrusions or recesses that form an air flow directed toward the outer periphery of the central force of the shroud along the surface during operation of the fan.
  • the projecting portion or the recessed portion formed on the surface of the shroud with respect to the bell mouth generates an air flow directed toward the outer periphery of the central force of the shroud along the surface.
  • the outer force of the shroud also passes through the surface of the outer wall of the bell mouth, and the center force of the shroud is again directed toward the outer periphery. Power develops into a circulating airflow. For this reason, a part of the air flow that is also discharged by the fan outlet force is attracted by this circulating air flow and circulates.
  • Part of the air circulating in this manner flows from the gap between the hub and the shroud along the surface of the shroud main plate along the surface of the shroud urgingly toward the fan outlet, so that the air flow along the surface of the shroud main plate flows.
  • the separation flow generated in the vicinity of the fan outlet on the surface of the main plate of the shroud is suppressed, the operating sound of the centrifugal fan is reduced, and the wind speed distribution in the blade height direction at the fan outlet is uniform. It becomes.
  • a surface of the shroud with respect to the bell mouth is formed with a plurality of rib-like protrusions that form an air current flow from the center of the shroud to the outer periphery along the surface during operation of the fan.
  • the rib-like protrusion it is easy to cause the rib-like protrusion to act in the same manner as the blade, and compared to the case where a groove-like recess is formed on the surface of the shroud with respect to the bell mouth, the center of the shroud is formed. Counterforce on the outer periphery It becomes easier to generate a circulating airflow.
  • the rib-shaped protrusions on the surface of the shroud with respect to the bell mouth have substantially the same inclination as the chamber line of the shroud-side blade element of the blade, and are formed at equal intervals around the entire surface of the shroud with respect to the bell mouth. It is preferable. According to this configuration, the airflow direction of the circulating airflow formed on the surface of the shroud with respect to the bell mouth can be matched with the airflow direction of the airflow discharged from the fan outlet. Therefore, the air flow force discharged from the fan outlet The amount attracted by the circulating airflow on the surface increases. As a result, the air flow at the shroud suction loca also increases toward the fan outlet along the surface of the shroud main plate, and the separation flow generated near the fan outlet on the surface of the shroud main plate is further suppressed. can do.
  • the pitch of the rib-shaped protrusions on the surface of the shroud with respect to the bell mouth is preferably smaller than the pitch of the blades. According to this configuration, a circulating air current can be efficiently generated in the space between the surface of the shroud with respect to the bell mouth and the bell mouth.
  • the height of the rib-like protrusion on the surface of the shroud with respect to the bell mouth is preferably about the same as the thickness of the shroud. According to this configuration, when the shroud is integrally molded with the resin, the change in the thickness of the entire shroud can be reduced, and the shroud can be easily molded. In addition, the rib-like protrusions of the shroud have an appropriate height with respect to a small space formed between the shroud and the bell mouth. As a result, it is possible to efficiently reduce the noise by efficiently generating the circulating airflow.
  • the rib-shaped protrusion on the surface of the shroud against the bell mouth is formed by a surface force against the bell mouth of the shroud that extends vertically and is positioned forward in the rotational direction of the impeller, and a surface force of the shroud against the bell mouth. It is preferable to have a rear side surface that extends vertically and is located rearward in the rotational direction of the impeller, and a front end surface that connects both side surfaces. In this case, the front end surface and the front side surface are connected so as to be substantially orthogonal to each other, and the rear side surface is curved toward the front side surface toward the front end.
  • an air conditioner equipped with the centrifugal fan is provided. According to this configuration, since the operation sound of the centrifugal fan is reduced, the noise of the air conditioner is reduced. Can be reduced.
  • an air suction port for sucking and sucking room air is formed in front of the fan suction port of the centrifugal fan.
  • a heat exchanger is arranged on the outlet side of the centrifugal fan.
  • An air outlet that blows air into the room is located downstream of the heat exchanger.
  • the centrifugal fan is preferably a turbo fan. According to this configuration, the fan efficiency can be improved and the driving noise can be further suppressed.
  • FIG. 1 is a perspective view showing an external appearance of an air conditioner according to an embodiment of the present invention.
  • FIG. 2 is a plan sectional view showing an air conditioner.
  • FIG. 3 is a perspective view showing a state where the front surface of the air conditioner is opened.
  • FIG. 4 is a perspective view showing an impeller constituting a turbo fan of an air conditioner.
  • FIG. 5 is an enlarged perspective view showing a part of the impeller.
  • FIG. 6 is an enlarged longitudinal sectional view showing a part of a turbofan.
  • FIG. 7 is an enlarged cross-sectional view showing a rib-like protrusion in the impeller.
  • FIG. 8 is a cross-sectional view showing a modification of the rib-like protrusion.
  • FIG. 9 is a perspective view showing a heat exchanger in the air conditioner.
  • FIG. 10 is a perspective view showing an impeller in a turbofan according to a conventional example.
  • FIG. 11 is a longitudinal sectional view showing a part of a turbofan.
  • centrifugal fan according to an embodiment of the present invention and an air conditioner equipped with the centrifugal fan will be described with reference to the drawings.
  • the air conditioner according to the present embodiment is an indoor unit of a wall-mounted air conditioner, and has a horizontally long box shape as shown in the perspective view of FIG. This indoor unit is formed so that the dimension in the thickness direction (vertical direction in FIG. 2) is reduced as shown in the plan view of FIG. Yes.
  • the main casing 1 houses a turbo fan 2 as an indoor fan and a heat exchanger 4 that cools or heats indoor air.
  • the main body casing 1 is provided with a front plate 11 on the front surface of the main body casing 1.
  • the front plate 11 is provided with an air inlet 12 for sucking indoor air at the center, and air outlets 13 for blowing out the air heat-exchanged by the heat exchanger 4 on both sides.
  • the turbo fan 2 is arranged at the center and the heat exchanger 4 is arranged on both sides.
  • the turbo fan 2 is arranged so that the air sucked from the air inlet 12 is blown out to the side of the turbo fan 2.
  • the heat exchanger 4 is located on the blowout side of the turbo fan 2.
  • An air passage 14 is formed in the main body casing 1 so that the air sucked into the turbofan 2 is heat-exchanged by the heat exchanger 4 and then blown out into the room through the air outlet 13.
  • the turbofan 2 includes an impeller 21, a bell mouth 22 that guides air to the impeller 21, and a motor 23 that drives the impeller 21.
  • the rotating shaft of the impeller 21, that is, the rotating shaft 23 a of the motor 23 is arranged at the center in the main casing 1 so as to extend in the thickness direction of the main casing 1.
  • the bell mouth 22 is disposed at a position corresponding to the air inlet 12.
  • a thin motor for example, a print motor is used, and is fixed at a position corresponding to the impeller 21 on the back wall of the main body casing 1.
  • the impeller 21 is disposed so as to face the main plate 25, the hub 24 that fixes the rotating shaft 23a of the motor 23, the main plate 25 integrally formed on the outer periphery of the hub 24, and the like. And a shroud 27 forming a gas flow path 26, and six blades 28 disposed between the main plate 25 and the shroud 27.
  • FIG. 4 is a perspective view showing the outer appearance of the impeller
  • FIG. 5 is an enlarged perspective view showing a part of the impeller
  • FIG. 6 is a longitudinal sectional view showing a part of the turbofan.
  • An arrow R in FIGS. 3 to 5 and FIGS. 7 and 8 to be described later indicates the rotation direction of the impeller 21.
  • a fan suction port 29 is formed at the center of the bell mouth 22.
  • the bell mouth 22 also functions as a partition wall that partitions the suction side of the heat exchange 4 in cooperation with the front plate 11.
  • Shroud 2 in gas flow path 26 A portion corresponding to the outer periphery of 7, that is, a rear edge of the blade 28 constitutes a fan outlet 30.
  • the configuration of the blade 28 is the same as the configuration of the blade described in Patent Document 1 described above. That is, the vane 28 is offset by a predetermined amount on the opposite side in the rotational direction from the position of the coupling portion with the main plate 25 at the trailing edge.
  • the pressure surface of the shroud-side blade element is formed in a projecting shape, and the maximum warp position of the camber line of the shroud-side blade element is located at the leading edge of the intermediate position of the chord length.
  • the shroud-side blade inlet angle is formed at the same angle as when the shroud-side blade blade camber wire is a single-arc camber wire, and the main plate-side blade element camber wire has a single-arc shape. Yes.
  • the surface 27a of the shroud 27 with respect to the bell mouth 22 forms a directional airflow around the central force of the shroud 27 along the surface 27a during the operation of the fan.
  • a plurality of rib-like protrusions 31 are formed. These rib-shaped protrusions 31 are formed so as to have substantially the same inclination as the camber line of the shroud-side blade element of the blade 28, and are formed at equal intervals over the entire circumference of the surface 27 a of the shroud 27.
  • the pitch of each rib-like protrusion 31 is formed as small as about 1Z10 of the pitch of each blade 28.
  • the height of the rib-like protrusion 31 is about the same as the thickness of the shroud 27 and is about 1 mm.
  • the rib-shaped protrusion 31 connects the front side surface 32 positioned in the front, the rear side surface 33 positioned rearward, and both side surfaces 32 and 33 in the rotational direction of the impeller 21. And a leading end face 34.
  • Each side surface 32, 33 extends vertically from the surface 27 a of the shroud 27.
  • the front side surface 32 and the front end surface 34 are connected so as to be substantially orthogonal to each other.
  • the rear side surface 33 is curved toward the front side surface 32 according to the direction of force at the tip.
  • the heat exchangers 4 are arranged approximately symmetrically via the turbofan 2. As shown in the perspective view of FIG. 9, the two heat exchangers 4 arranged in a distributed manner are connected by a refrigerant pipe 41 arranged using the space at the bottom of the main body casing 1 so that they function as a unit. It is configured.
  • a refrigerant pipe 41 arranged using the space at the bottom of the main body casing 1 so that they function as a unit. It is configured.
  • six rows of flat tubes 44 extend between the front plate 42 and the rear plate 43 so as to extend in the thickness direction of the main casing 1 and to each other. They are arranged in parallel.
  • Corrugated fins 45 are interposed between the flat tubes 44 and between the flat tubes 44 and the front plate 42 or the rear plate 43. The flat tube 44 and the corrugated fin 45 are joined together by brazing, for example.
  • the air conditioner configured as described above and the turbofan mounted on the air conditioner operate as follows.
  • room air is sucked from the air inlet 12.
  • This indoor air is also taken into the gas flow path 26 of the turbofan 2 by the fan suction port 29, is pressurized by the blades 28, and is discharged from the fan outlet 30.
  • the air blown out from the fan blowout port 30 is heat-exchanged by each heat exchange 4 and blown out into the room from the air blowout port 13.
  • the plurality of rib-shaped protrusions 31 formed on the surface 27a of the shroud 27 act like blades, and the shroud along the surface 27a.
  • the central force of 27 is also directed toward the outer periphery.
  • Air flow S1 is generated.
  • this air flow S1 is again transmitted from the outer periphery of the shroud 27 through the surface of the outer peripheral wall of the bell mouth 22 from the center of the shroud 27. It develops into a circulating airflow S2 toward the outer periphery.
  • the air flow S4 force that is a part of the air flow S3 discharged from the fan outlet 30 is attracted to the circulating air flow S2 and circulates.
  • the air flow S4, which is a part of the circulating air flows from the gap 35 between the hub 24 and the shroud 27 toward the fan outlet 30 along the surface 27b with respect to the main plate 25 of the shroud 27. Therefore, the air flow S5 along the surface 27b of the shroud 27 increases.
  • the separation flow E generated in the vicinity of the fan outlet 30 on the surface 27b of the shroud 27 is suppressed, the operation sound of the turbo fan 2 is reduced, and the wind speed in the height direction of the blades at the fan outlet 30 is reduced. Distribution is made uniform.
  • the rib-like protrusion 31 is formed to have substantially the same inclination as the camber line of the shroud side blade element of the blade 28. Therefore, the airflow direction of the airflow S1 flowing along the surface 27a of the shroud 27 in the outer peripheral portion of the shroud 27 and the airflow direction of the airflow S3 discharged from the fan outlet 30 can be matched. In this way, the airflow directions of the airflow S1 and the airflow S3 substantially match, so that the airflow discharged from the fan outlet 30 S3 force Airflow S4 attracted by the circulating airflow S2 on the surface 27a of the shroud 27 The amount of increases.
  • the suction loca of the shroud 27 is also blown out along the surface 27b of the shroud 27.
  • the air flow S5 force S increases toward the port 30 and the separated flow E generated near the fan outlet 30 on the surface 27b of the shroud 27 can be further suppressed.
  • the rib-shaped protrusions 31 are formed so that the pitch is considerably smaller than the pitch of the blades 28. Therefore, in the small space between the surface 27a of the shroud 27 and the bell mouth 22, the circulating air flow S2 can be generated efficiently.
  • the height of the rib-like protrusion 31 is approximately the same as the thickness of the shroud 27. Therefore, when the entire shroud 27 is integrally molded with resin, the amount of change in the thickness of the entire shroud 27 can be reduced, and the molding of the shroud 27 becomes easy.
  • the rib-shaped protrusion 31 has an appropriate height with respect to a small space formed between the shroud 27 and the bell mouth 22, and efficiently generates the circulating air flow S2 to generate noise. It can be reduced efficiently.
  • the rib-shaped protrusion 31 has a front side surface 32 positioned on the pressure side extending vertically to the tip end surface 34, and a force that acts on the outer periphery of the central force on the surface 27 a of the shroud 27. It is possible to maintain a high generation capacity of the opposing airflow S1. Further, the front end portion of the rear side surface 33 located on the negative pressure side is formed in an arc shape. For this reason, air easily flows around to the negative pressure side, and the generation of vortex F on the negative pressure side can be suppressed. As a result, the central force on the surface 27a of the shroud 27 can generate a counter-current airflow more efficiently on the outer periphery, and noise caused by vortices generated on the negative pressure side can be suppressed.
  • the position force of the joint portion with the shroud 27 at the rear edge portion of the blade 28 is less than the joint portion with the main plate 25. It is offset by a predetermined amount on the opposite side of the rotational direction from the position. Therefore, a force in the direction of the shroud 27 is applied to the air flow that flows in the direction toward the rear edge of the blade 28 by flowing in the force at the front edge of the blade 28. Therefore, this point force also suppresses the separation flow E.
  • the pressure surface of the shroud blade element is formed in a projecting shape, and the maximum warp position of the camber wire of the shroud blade element is located at the leading edge from the intermediate position of the chord length.
  • the blade inlet angle on the shroud side is formed at the same angle as when the camber wire of the shroud blade blade element is a single arc camber wire, and the camber wire of the main plate blade element has a single arc shape. is doing. This increases the blade outlet angle on the shroud side, The blade exit angle is close to the blade exit angle on the main plate side.
  • the air conditioner according to the present embodiment can reduce the operation sound of the turbo fan 2, and thus can reduce the operation sound as an air conditioner.
  • This air conditioner has an air suction port 12 for sucking room air in front of the fan suction port 29 of the turbo fan 2.
  • a heat exchanger 4 is arranged on the blow-out side of the turbo fan 2, and an air outlet 13 for blowing air into the room is arranged downstream of the heat exchanger 4. Therefore, by reducing the size of the heat exchanger 4 in the thickness direction of the main casing 1, it becomes possible to reduce the outer dimension in the thickness direction of the air conditioner.
  • the wind speed distribution in the height direction of the blades at the fan outlet 30 of the turbo fan 2 is made uniform, and the wind speed distribution of the heat exchange 4 is improved. As a result, the heat exchange efficiency of the heat exchanger 4 is improved, the resistance in the air conditioner is reduced, and the energy efficiency of the air conditioner is improved.
  • a turbo fan 2 is used as an indoor fan. Therefore, fan efficiency can be improved and operation noise can be further suppressed as compared with the case where other centrifugal fans are used.
  • the blade 28 has the same configuration as the blade described in Patent Document 1 described above.
  • the present invention is not limited to this.
  • the front and rear edges of the blade 28 have a two-dimensional shape perpendicular to the main plate 25 and the shroud 27, respectively. 28 may have. In this case as well, the present invention can be applied.
  • a protrusion having a blade shape forming the air flow si or a recess such as a groove may be formed on the surface 27a of the shroud 27.
  • the groove can be easily formed by cutting, but a deep groove cannot be obtained due to the thickness of the shroud 27.
  • the air flow changes more than in the case of the rib-shaped protrusion 31, and the central force of the shroud 27 is also directed toward the outer periphery along the surface 27a of the shroud 27. It is difficult to efficiently generate the air flow S1. I think that the.
  • the front end surface 34 and the front side surface (positive pressure surface) 32 are connected so as to be substantially orthogonal to each other, and the front end surface 34 and the rear side surface
  • the negative pressure surface 33 may be connected so as to be substantially orthogonal to each other.
  • the generation of vortex F increases, and compared with the rib-like convex portion 31 in the present embodiment, noise is increased.
  • the reduction effect and the uniform wind speed distribution at the fan outlet deteriorate.
  • the height of the rib-like protrusion 31 is approximately lmm in the present embodiment.
  • the height of the rib-shaped protrusion 31 is appropriately changed according to the diameter of the impeller of the turbofan 2 or the size of the space formed between the shroud 27 and the bell mouth 22. May be.
  • the rib-shaped protrusion 31 is excessively high relative to the size of the space formed between the shroud 27 and the bell mouth 22, the eddy current generated around the rib-shaped protrusion 31 is large. Thus, the noise reduction effect is impaired.
  • This embodiment is a wall-mounted air conditioner!
  • the present invention is not limited to this, and the present invention may be applied to an air conditioner having a form other than the form of the present embodiment.
  • the present invention is suitable, for example, for a compact ceiling-embedded type.
  • a heat exchanger having a form other than the form of the present embodiment for example, a cross fin coil heat exchanger may be used. .
  • the air conditioner is not limited to the structure in which the heat exchange is arranged on the blow-out side of the turbo fan 2 as a centrifugal fan, but is different from the air conditioner in which the heat exchange 4 is arranged on the suction side of the turbo fan 2.
  • the centrifugal fan according to the present invention may be applied. Industrial applicability
  • the centrifugal fan according to the present invention is one of a turbo fan, a sirocco fan, a radial fan, and the like. It can be applied to a general centrifugal fan.
  • the air conditioner equipped with this centrifugal fan can be applied to various types of air conditioners for home use and business 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)

Abstract

La présente invention concerne un ventilateur centrifuge où la distribution de vitesse d’écoulement d’air au niveau d’une ouverture de sortie de ventilateur, dans la direction de la hauteur d’une pale, est uniformisée pour réduire le bruit de fonctionnement, et un climatiseur dans lequel le ventilateur centrifuge est utilisé pour réduire le bruit de fonctionnement. Le ventilateur centrifuge comporte un moyeu pour fixer l’arbre rotatif d’un moteur, une plaque principale formée au niveau de la circonférence extérieure du moyeu, un capot de refoulement placé pour faire face à la plaque principale pour former un passage d’écoulement d’air, des pales placées entre la plaque principale et le capot de refoulement, et un orifice évasé placé sur le côté aspiration du capot de refoulement. Des crêtes ou évidements sont formés dans cette surface du capot de refoulement qui fait face à l’orifice évasé, et les crêtes ou évidements forment, durant le fonctionnement du ventilateur, un écoulement d’air le long de la surface à partir du centre du capot de refoulement vers sa circonférence extérieure. Le climatiseur comporte le ventilateur centrifuge décrit ci-dessus.
PCT/JP2006/318932 2005-09-30 2006-09-25 Ventilateur centrifuge et climatiseur associé WO2007040073A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP06810500.6A EP1933039A4 (fr) 2005-09-30 2006-09-25 Ventilateur centrifuge et climatiseur associé
AU2006298249A AU2006298249B2 (en) 2005-09-30 2006-09-25 Centrifugal fan and air conditioner using the same
KR1020087006553A KR100934556B1 (ko) 2005-09-30 2006-09-25 원심 팬 및 이것을 이용한 공기 조화기
US11/992,645 US20090255654A1 (en) 2005-09-30 2006-09-25 Centrifugal Fan and Air Conditioner Using the Same

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-289208 2005-09-30
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

Publications (1)

Publication Number Publication Date
WO2007040073A1 true WO2007040073A1 (fr) 2007-04-12

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Country Status (7)

Country Link
US (1) US20090255654A1 (fr)
EP (1) EP1933039A4 (fr)
JP (1) JP4017003B2 (fr)
KR (1) KR100934556B1 (fr)
CN (1) CN100559032C (fr)
AU (1) AU2006298249B2 (fr)
WO (1) WO2007040073A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015111210A1 (fr) * 2014-01-27 2015-07-30 三菱電機株式会社 Ventilateur centrifuge et dispositif de climatisation

Families Citing this family (26)

* 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
SI2218917T1 (sl) * 2009-02-12 2013-05-31 Ebm-Papst Mulfingen Gmbh & Co. Kg Radialno ali diagonalno ventilatorsko kolo
DE202009018770U1 (de) 2009-02-12 2013-03-07 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
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
DE102010023017A1 (de) * 2010-06-08 2011-12-08 Georg Emanuel Koppenwallner Buckelwalgebläse, Verfahren zur örtlichen Verbesserung der Strömung bei Strömungsmaschinen und Fahrzeugen
ITTO20110362A1 (it) 2011-04-26 2012-10-27 Denso Corp Gruppo ventilatore per veicoli
WO2014125710A1 (fr) * 2013-02-12 2014-08-21 三菱電機株式会社 Unité de refroidissement extérieure pour dispositif de climatisation pour véhicule
US9618010B2 (en) 2013-04-22 2017-04-11 Lennox Industries Inc. Fan systems
CN103267319B (zh) * 2013-06-15 2015-12-30 邓明义 一种隐藏式空调器室内机
WO2015190077A1 (fr) * 2014-06-11 2015-12-17 パナソニックＩｐマネジメント株式会社 Unité de conditionnement de température, système de conditionnement de température, et véhicule équipé de ladite unité de conditionnement de température
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
US20200127345A2 (en) * 2015-07-24 2020-04-23 Panasonic Intellectual Property Management Co., Ltd. Temperature conditioning unit, temperature conditioning system, and vehicle
EP3557145B1 (fr) * 2016-12-19 2023-10-18 Mitsubishi Electric Corporation Dispositif de climatisation
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
WO2019116838A1 (fr) * 2017-12-13 2019-06-20 三菱電機株式会社 Unité d'échange de chaleur et dispositif de climatisation dans lequel celle-ci est montée
CN110454418A (zh) * 2018-05-07 2019-11-15 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
JP2023554328A (ja) * 2020-12-10 2023-12-27 イノーヴァ エス．アール．エル． 改善されたファンコイルユニット
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 (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5186666U (fr) * 1974-12-30 1976-07-12
JPS5332406A (en) * 1976-09-08 1978-03-27 Hitachi Ltd Vane wheel
JPS61145899U (fr) * 1985-03-01 1986-09-09
JPH04179899A (ja) * 1990-11-14 1992-06-26 Matsushita Electric Ind Co Ltd 電動送風機
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
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

Family Cites Families (20)

* 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 (fr) * 1973-05-18 1975-01-18
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
DE3627778A1 (de) * 1986-08-16 1988-02-18 Bbc Brown Boveri & Cie Beruehrungsfreie zentrifugaldichteinrichtung fuer einen rotierenden maschinenteil
WO1988002820A1 (fr) * 1986-10-07 1988-04-21 Warman International Limited Turbines pour pompes centrifuges
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
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
US7244099B2 (en) * 2003-05-01 2007-07-17 Daikin Industries, Ltd. Multi-vane centrifugal fan
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
US20050191174A1 (en) * 2004-02-27 2005-09-01 Ling-Zhong Zeng Centrifugal fan

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5186666U (fr) * 1974-12-30 1976-07-12
JPS5332406A (en) * 1976-09-08 1978-03-27 Hitachi Ltd Vane wheel
JPS61145899U (fr) * 1985-03-01 1986-09-09
JPH04179899A (ja) * 1990-11-14 1992-06-26 Matsushita Electric Ind Co Ltd 電動送風機
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1933039A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015111210A1 (fr) * 2014-01-27 2015-07-30 三菱電機株式会社 Ventilateur centrifuge et dispositif de climatisation
JPWO2015111210A1 (ja) * 2014-01-27 2017-03-23 三菱電機株式会社 遠心ファン及び空気調和装置

Also Published As

Publication number Publication date
CN101253333A (zh) 2008-08-27
EP1933039A1 (fr) 2008-06-18
US20090255654A1 (en) 2009-10-15
JP2007100548A (ja) 2007-04-19
JP4017003B2 (ja) 2007-12-05
CN100559032C (zh) 2009-11-11
AU2006298249B2 (en) 2010-02-18
KR20080037722A (ko) 2008-04-30
AU2006298249A1 (en) 2007-04-12
EP1933039A4 (fr) 2014-05-07
KR100934556B1 (ko) 2009-12-29

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