WO2009139422A1 - Ventilateur centrifuge - Google Patents

Ventilateur centrifuge Download PDF

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Publication number
WO2009139422A1
WO2009139422A1 PCT/JP2009/058938 JP2009058938W WO2009139422A1 WO 2009139422 A1 WO2009139422 A1 WO 2009139422A1 JP 2009058938 W JP2009058938 W JP 2009058938W WO 2009139422 A1 WO2009139422 A1 WO 2009139422A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
main plate
centrifugal blower
air
impeller
Prior art date
Application number
PCT/JP2009/058938
Other languages
English (en)
Japanese (ja)
Inventor
真吾 大山
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to US12/921,828 priority Critical patent/US20110023526A1/en
Priority to JP2010512006A priority patent/JPWO2009139422A1/ja
Priority to EP09746628A priority patent/EP2275689A1/fr
Priority to AU2009247219A priority patent/AU2009247219A1/en
Priority to CN2009801123504A priority patent/CN101990604A/zh
Publication of WO2009139422A1 publication Critical patent/WO2009139422A1/fr

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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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade

Definitions

  • the present invention relates to a centrifugal blower, and more particularly, to a structure of an impeller blade of a centrifugal blower.
  • centrifugal fans such as turbofans have a problem of large noise, so it is a problem to reduce noise. Therefore, various technologies have been developed so far in the centrifugal blower in order to reduce the blowing sound. As a general design method for reducing the blowing noise, an increase in the outer diameter of the fan impeller can be mentioned.
  • the rotation speed of the fan impeller can be reduced by increasing the outer diameter of the fan impeller. Thereby, the flow velocity of the airflow blown from the fan impeller is reduced.
  • the blowing sound is proportional to the sixth power of the flow velocity.
  • a thick blade that is, an airfoil blade
  • an airfoil blade is used to reduce the separation of the airflow around the blade and to reduce noise at the lowest possible cost (for example, Patent Documents). 1).
  • the above technique is effective in a centrifugal fan whose blade width is sufficiently small with respect to the outer shape, as described in Patent Document 3. That is, by cutting out the blade, it is possible to prevent the suction airflow from separating near the side plate side of the blade, and to flow the airflow along the vicinity of the side plate side of the blade.
  • the blade width is sufficiently wide as in an ordinary centrifugal blower, that is, when the influence of peeling on the side plate side is not dominant, the above technique is not necessarily effective.
  • the ratio of the outer diameter on the main plate side of the impeller / the outer diameter on the side plate side of the impeller is set to 1.2 to 1.6 at the outlet of the impeller. Therefore, when the extension amount due to the expansion of the blades is small, the noise reduction effect cannot be obtained, and conversely, when the extension amount is too large, the flow rate characteristic is deteriorated.
  • the outer diameter on the main plate side of the impeller is expanded by 20% relative to the outer diameter on the side plate side. This does not provide an advantage over a technology that simply enlarges the fan diameter and simply enlarges the fan. In the first place, the increase in size by more than 20% cannot solve the problem of the reduction in size and noise that is the conventional problem at all.
  • an impeller employing a three-dimensional blade extending in the direction of the rotation axis of the fan while twisting from the main plate to the side plate has also been proposed (see, for example, Patent Document 2).
  • the impeller that employs such a three-dimensional blade the load distribution on the surface of the blade and the pressure of the airflow passing between the blades are compared to those employing the two-dimensional blade as described above. Variability is improved.
  • FIG. 25 shows an air conditioner 1 that employs a centrifugal blower having an impeller.
  • the air conditioner 1 is a ceiling-embedded air conditioner, and includes a casing 2 that houses various components therein, and a decorative panel 3 that is disposed below the casing 2. More specifically, the casing 2 of the air conditioner 1 is inserted into an opening formed in the ceiling U of the air conditioning room, and the decorative panel 3 is disposed along the ceiling U.
  • the casing 2 is a box-like body having an opening below, and has a substantially octagonal shape in which long sides and short sides are alternately arranged in a plan view.
  • the casing 2 has a substantially octagonal top plate 21 in which long sides and short sides are alternately formed, and a side wall plate 22 extending downward from the periphery of the top plate 21.
  • the decorative panel 3 is a substantially quadrangular plate in plan view.
  • the decorative panel 3 is positioned substantially in the center and is formed to correspond to each of the four sides of the air inlet 31 for sucking air in the air-conditioned room, and a plurality of air outlets for blowing air from the casing 2 into the air-conditioned room. 32.
  • Each side of the decorative panel 3 is disposed so as to correspond to each long side of the top plate 21 of the casing 2.
  • Each air inlet 31 is a substantially square opening.
  • each air outlet 32 is a rectangular opening extending along the direction along each side of the decorative panel 3.
  • the air inlet 31 is provided with an air inlet grill 33 and a filter 34 for removing dust in the air sucked from the air inlet 31.
  • each air outlet 32 is provided with a horizontal flap 35 that can swing around an axis extending along the longitudinal direction of the air outlet 32.
  • the horizontal flap 35 is a rectangular blade member extending in the longitudinal direction of each air outlet 32.
  • each horizontal flap 35 rotates the shaft support pins provided at both ends in the longitudinal direction thereof by a motor (not shown), so that the air blown out from the air outlet 32 toward the air-conditioned room. Change the wind direction.
  • a blower 4 that mainly sucks air in the air-conditioned room into the casing 2 through the air inlet 31 of the decorative panel 3 and blows it out in the outer peripheral direction, and is arranged so as to surround the outer periphery of the blower 4.
  • a heat exchanger 6 is arranged inside the casing 2.
  • the blower 4 is a turbo fan as an example of a centrifugal blower targeted by the present invention.
  • the blower 4 is connected to a fan motor (impeller driving means) 41 provided downward in the center of the top plate 21 of the casing 2 and a shaft (rotary shaft) 41 a of the fan motor 41 and is rotated.
  • An impeller 42 is provided below in the center of the top plate 21 of the casing 2 and a shaft (rotary shaft) 41 a of the fan motor 41 and is rotated.
  • An impeller 42 is a turbo fan as an example of a centrifugal blower targeted by the present invention.
  • the blower 4 is connected to a fan motor (impeller driving means) 41 provided downward in the center of the top plate 21 of the casing 2 and a shaft (rotary shaft) 41 a of the fan motor 41 and is rotated.
  • An impeller 42 is provided downward in the center of the top plate 21 of the casing 2 and a shaft (rotary shaft) 41 a of the fan motor 41 and is rotate
  • the heat exchanger 6 is a cross fin tube type heat exchanger that is formed by being bent in a substantially square shape so as to surround the outer periphery of the blower 4.
  • a refrigerant pipe is connected to an outdoor unit (not shown) installed outdoors. Connected through.
  • the heat exchanger 6 functions as an evaporator during cooling operation and as a condenser during heating operation. As a result, the heat exchanger 6 exchanges heat with the air sucked into the casing 2 through the air suction port 31 by the blower 4, and cools the air during the cooling operation, while cooling the air during the heating operation. Heat.
  • a drain pan 7 for receiving drain water generated by condensation of moisture in the air on the surface of the heat exchanger 6 is disposed below the heat exchanger 6.
  • the drain pan 7 is attached to the lower part of the casing 2.
  • the drain pan 7 further includes an air suction hole portion 71 formed so as to communicate with the air suction port 31 of the decorative panel 3, and an air outlet hole portion formed so as to correspond to the air outlet 32 of the decorative panel 3. 72 and a drain water receiving groove 73 for receiving drain water formed so as to cover the lower portion of the heat exchanger 6.
  • a bell mouth 5 for guiding the air sucked from the air suction port 31 of the decorative panel 3 to the impeller 42 of the blower 4 is disposed in the air suction hole portion 71 of the drain pan 7.
  • FIG. 26 is an external perspective view of the impeller 42.
  • FIG. 27 is a side view of the impeller 42 of FIG.
  • the impeller 42 mainly includes a disk-shaped main plate 43, an annular side plate 45 disposed at a distance from the main plate 43, and a plurality of blades 44 disposed between the main plate 43 and the side plate 45. .
  • the main plate 43 is connected to the shaft 41a of the fan motor 41 described above.
  • the plurality of blades 44 are disposed along the main plate 43 at a predetermined angle with the shaft 41a of the fan motor 41 as the central axis.
  • the main plate 43 is a resin member.
  • a substantially frustoconical convex portion 43 a is formed at the central portion of the main plate 43 so as to protrude toward the air suction port 31.
  • a main plate cover 46 is fixed to the lower surface of the main plate 43 so as to be disposed at a predetermined interval from the main plate 43 and cover the cooling air holes.
  • a plurality of guide blades 46 a extending radially are provided on the surface of the main plate cover 46 that faces the main plate 43.
  • the side plate 45 has a diameter that gradually decreases from the outer periphery toward the central opening.
  • the side plate 45 is a bell-shaped resin member that protrudes toward the air inlet 31.
  • FIG. 28 is a perspective view of the blade 44 as viewed from the left rear.
  • FIG. 29 is a projection view of the blade 44 of FIG. 28 as viewed from above.
  • 30 is a side view in which a plurality of cutting lines 31A-31A to 31E-31E are inserted into the blade 44 of FIG. 31 (a) to 31 (e) are cross-sectional views taken along lines 31A-31A to 31E-31E in FIG. 30, respectively.
  • FIG. 32 is an explanatory view showing the operation of the blade 44.
  • Each of the blades 44 is a resin member formed separately from the main plate 43 and the side plate 45 described above. One end surface of each blade 44 is fixed to the main plate 43, and the other end surface of each blade 44 is fixed to the side plate 45. In the side view of the impeller 42, each blade 44 is inclined with the end on the side plate 45 side inclined behind the end on the main plate 43 side as shown in FIG. 28. Further, as shown in FIG. 29, each blade 44 is formed so that these end portions intersect with each other in a substantially X shape. That is, the blade 44 has a three-dimensional shape extending in parallel with the rotation axis while being twisted between the main plate 43 and the side plate 45.
  • the front end in the rotational direction of the blade 44 which is the three-dimensional blade, that is, the front edge 44a extends from the end on the main plate 43 side to a predetermined position on the side plate 45 side so as to have substantially the same radius.
  • the blade 44 has an inclined edge that recedes outward so that the radius gradually decreases from a predetermined position on the side plate 45 side to the side plate 45.
  • the end of the blade 44 in the direction opposite to the rotation direction R that is, the rear edge 44b has a shape in which the position on the main plate 43 side and the position on the side plate 45 side are connected by a straight line extending parallel to the rotation.
  • the load distribution on the surface of the blade 44 and the distance between the blades 44 are compared with the blade shape made on the basis of the blade element drawn in a plane like Patent Documents 1, 3, and 4 described above.
  • the pressure fluctuation of the airflow passing through the air is greatly improved. Therefore, at least noise caused by air pressure fluctuation is effectively reduced.
  • the rear edge 44b of the blade 44 has a shape in which both ends are linearly connected between the main plate 43 and the side plate 45, there is still a problem that noise due to the influence of the wake vortex is generated.
  • the air flow F 2 flowing along the rounded surface of the side plate 45 out of the air flow sucked from the vicinity of the side plate 45 of the blade 44 is small.
  • the original main flow F 1 having a large flow rate sucked from the center of the side plate 45 flows in the vicinity of the main plate 43 due to the relationship between the flow velocity vectors. Therefore, the wind speed distribution of the blown airflow at the exit portion of the blade 44 is not uniform in the span direction of the blade 44.
  • An object of the present invention is to provide a centrifugal fan that can further reduce noise with respect to a three-dimensional blade used in the centrifugal fan.
  • a plurality of three-dimensional blades and a span end direction of each blade are fixed at predetermined intervals in the circumferential direction.
  • a centrifugal blower comprising a main plate, a ring-shaped side plate provided on the other end surface of each blade in the span direction, and blade driving means for rotating the blade via the main plate,
  • a centrifugal blower is provided in which the radial length of the outer peripheral end portion on the main plate side is set longer than the radial length of the outer peripheral end portion on the side plate side of each blade.
  • the velocity distribution of the mainstream portion of the airflow that flows biased toward the main plate side portion of the blade is greatly improved. Therefore, the static pressure-flow rate characteristic of the blower is improved in the entire flow rate range, and the blown amount is increased. Moreover, the specific noise characteristic of the blower is also greatly improved, and the influence of the wake vortex generated at the blade trailing edge on the three-dimensional blade main plate side can be relatively reduced. As a result, noise caused by the wake vortex is effectively reduced.
  • the airflow passing through each blade is It is preferable that work on the main plate side of the blade is effectively received from the blade, and the velocity of the airflow in the span direction of each blade is effectively developed in the main plate side portion of each blade.
  • the velocity distribution of the mainstream portion of the airflow that flows biased toward the main plate side portion of the blade is greatly improved. Therefore, the static pressure-flow rate characteristic of the blower is improved in the entire flow rate range, and the blown amount is increased. Moreover, the specific noise characteristic of the blower is also greatly improved, and the influence of the wake vortex generated at the blade trailing edge on the three-dimensional blade main plate side can be relatively reduced. As a result, noise caused by the wake vortex is effectively reduced.
  • the radial length of the outer peripheral end of the blade on the main plate side is extended in the radial direction of the outer peripheral end of the blade on the side plate side by extending the trailing edge of the blade toward the rear of the air flow. It is preferably formed longer than the length.
  • the velocity distribution of the main flow portion of the airflow that is biased toward the main plate side of the blade is greatly improved. Therefore, the static pressure-flow rate characteristic of the blower is improved in the entire flow rate range, and the blown amount is increased. Moreover, the specific noise characteristic of the blower is also greatly improved, and the influence of the wake vortex generated at the blade trailing edge on the three-dimensional blade main plate side can be relatively reduced. As a result, noise caused by the wake vortex is effectively reduced.
  • the trailing edge is preferably extended so as to gradually become longer from the side plate toward the main plate.
  • the shape of the trailing edge of the blade becomes a substantially tapered shape that is enlarged from the side plate to the main plate. Therefore, the shape of the trailing edge of the blade can be made appropriate according to the change in the velocity distribution of the main flow that is biased toward the portion of the blade on the main plate side.
  • the substantially tapered shape that gradually expands from the side plate to the main plate may be either a linear change or a curved change.
  • the trailing edge may be extended in a curved shape, and a bulging portion may be formed at a portion on the main plate side of the trailing edge so that one or more inflection points exist in the curved portion.
  • the centrifugal blower forms a laminar shear layer under the influence of the airflow in the vicinity of the main plate due to the viscosity of the wall surface of the main plate. As a result, the main flow path is narrowed, and the fan performance may be reduced.
  • development of the said shear layer can be suppressed and fan performance can be improved.
  • the trailing edge is extended long backward corresponding to the velocity distribution of the main stream of the airflow at the trailing edge. According to such a configuration, the shape of the extended trailing edge can be made more appropriate according to the change in the mainstream speed distribution, and the fan performance can be further improved.
  • a step portion extended by a predetermined length in front of the blade is provided in a portion of the front edge of each blade on the main plate side.
  • the diameter of the main plate is enlarged in accordance with the extension of the blades.
  • the structural strength of the centrifugal fan can be improved at the same time by extending the diameter of the main plate.
  • the centrifugal blower is configured as a blower of an indoor unit for an air conditioner.
  • An air blower of an indoor unit for an air conditioner is essentially required to have a large air volume and quietness due to its characteristics. Therefore, the centrifugal blower of the present invention that is small in size, high in blowing performance, and low in noise is optimal as a blower for an indoor unit for an air conditioner.
  • centrifugal blower suitable for a blower of an indoor unit for an air conditioner that has a large air volume and is excellent in quietness and can be downsized.
  • FIG. 10 is a side view showing the blade of FIG. 6 together with a plurality of cutting lines 10A-10A to 10E-10E.
  • FIG. 35 is a graph showing changes in the static pressure coefficient as parameters for the flow rate coefficient for four examples, (a) is the conventional fan of FIGS.
  • FIG. 19 is an explanatory diagram showing the action of the blade.
  • FIG. 19 is a graph showing the change in specific noise with the flow coefficient as a parameter for the four examples in order to confirm the effect of the blade.
  • FIG. 19 (a) is a conventional blade of FIGS. (B) is a conventional blade of FIG. 25 to FIG. 32 provided with a step, (c) is the present embodiment of FIG. 1 to FIG. 12, and (d) is shown in FIG. 18 to FIG. This corresponds to the third modification of the present embodiment.
  • FIG. 19 is a graph showing changes in the static pressure coefficient with the flow coefficient as a parameter for the four examples of FIG. 22 in order to confirm the effect of the blade. Explanatory drawing which shows the effect
  • FIG. 29 is a projection view showing the blade of FIG. 28.
  • FIGS. 30A to 31E are cross-sectional views taken along lines 31A-31A to 31E-31E in FIG. Explanatory drawing which shows the effect
  • FIG. 1 shows the external appearance perspective view (ceiling part is abbreviate
  • the air conditioner 1 is a ceiling-embedded air conditioner, and includes a casing 2 that houses various components therein, and a decorative panel 3 that is disposed below the casing 2. More specifically, the casing 2 of the air conditioner 1 is inserted into an opening formed in the ceiling U of the air conditioning room, for example, as shown in FIG. 2 (vertical sectional view of the air conditioner 1). The decorative panel 3 is arranged along the ceiling U.
  • the casing 2 is a box-like body having an opening below, and has a substantially octagonal shape in which long sides and short sides are alternately arranged in a plan view.
  • the casing 2 has a substantially octagonal top plate 21 in which long sides and short sides are alternately formed, and a side wall plate 22 extending downward from the periphery of the top plate 21.
  • the decorative panel 3 is a substantially quadrangular plate in plan view.
  • the decorative panel 3 is positioned substantially in the center and is formed to correspond to each of the four sides of the air inlet 31 for sucking air in the air-conditioned room, and a plurality of air outlets for blowing air from the casing 2 into the air-conditioned room. 32.
  • Each side of the decorative panel 3 is disposed so as to correspond to each long side of the top plate 21 of the casing 2.
  • Each air inlet 31 is a substantially square opening.
  • each air outlet 32 is a rectangular opening extending along the direction along each side of the decorative panel 3.
  • the air inlet 31 is provided with an air inlet grill 33 and a filter 34 for removing dust in the air sucked from the air inlet 31.
  • each air outlet 32 is provided with a horizontal flap 35 that can swing around an axis extending along the longitudinal direction of the air outlet 32.
  • the horizontal flap 35 is a rectangular blade member extending in the longitudinal direction of each air outlet 32.
  • each horizontal flap 35 rotates the shaft support pins provided at both ends in the longitudinal direction thereof by a motor (not shown), so that the air blown out from the air outlet 32 toward the air-conditioned room. Change the wind direction.
  • a blower 4 that mainly sucks air in the air-conditioned room into the casing 2 through the air inlet 31 of the decorative panel 3 and blows it out in the outer peripheral direction, and is arranged so as to surround the outer periphery of the blower 4.
  • a heat exchanger 6 is arranged inside the casing 2.
  • the blower 4 is a turbo fan as an example of a centrifugal blower targeted by the present invention.
  • the blower 4 is connected to a fan motor (impeller driving means) 41 provided downward in the center of the top plate 21 of the casing 2 and a shaft (rotary shaft) 41 a of the fan motor 41 and is rotated.
  • An impeller 42 The detailed structure of the impeller 42 will be described later.
  • the heat exchanger 6 is a cross fin tube type heat exchanger that is formed by being bent in a substantially square shape so as to surround the outer periphery of the blower 4.
  • a refrigerant pipe is connected to an outdoor unit (not shown) installed outdoors. Connected through.
  • the heat exchanger 6 functions as an evaporator during cooling operation and as a condenser during heating operation. As a result, the heat exchanger 6 exchanges heat with the air sucked into the casing 2 through the air suction port 31 by the blower 4, and cools the air during the cooling operation, while cooling the air during the heating operation. Heat.
  • a drain pan 7 for receiving drain water generated by condensation of moisture in the air on the surface of the heat exchanger 6 is disposed below the heat exchanger 6.
  • the drain pan 7 is attached to the lower part of the casing 2.
  • the drain pan 7 further includes an air suction hole portion 71 formed so as to communicate with the air suction port 31 of the decorative panel 3, and an air outlet hole portion formed so as to correspond to the air outlet 32 of the decorative panel 3. 72 and a drain water receiving groove 73 for receiving drain water formed so as to cover the lower portion of the heat exchanger 6.
  • a bell mouth 5 for guiding the air sucked from the air suction port 31 of the decorative panel 3 to the impeller 42 of the blower 4 is disposed in the air suction hole portion 71 of the drain pan 7.
  • the air-conditioning apparatus 1 has the above-described configuration through the filter 34, the bell mouth 5, the drain pan 7, the blower 4, and the heat exchanger 6 from the air suction port 31 of the decorative panel 3.
  • the air flow paths leading to the four air outlets 32 are formed.
  • the air conditioner 1 can inhale the air in the air-conditioned room and exchange heat with the refrigerant in the heat exchanger 6 and then blow out the temperature-controlled air in all directions of the air-conditioned room through the air flow path. .
  • FIG. 3 is a perspective view showing an appearance of the impeller 42.
  • FIG. 4 is a side view showing the impeller 42 of FIG.
  • FIG. 5 is a view of the impeller 42 installed as shown in FIG. 4 as viewed from above.
  • the impeller 42 mainly includes a disk-shaped main plate 43, an annular side plate 45 disposed at a distance from the main plate 43, and a plurality of blades 44 disposed between the main plate 43 and the side plate 45. .
  • the main plate 43 is connected to the shaft 41a of the fan motor 41 described above.
  • the plurality of blades 44 are disposed along the main plate 43 at a predetermined angle with the shaft 41a of the fan motor 41 as the central axis.
  • the rotation direction of the impeller 42 is indicated by an arrow R in FIG.
  • the main plate 43 has an outer diameter Db ′.
  • the main plate 43 is a resin member.
  • a substantially frustoconical convex portion 43 a is formed at the central portion of the main plate 43 so as to protrude toward the air suction port 31.
  • a main plate cover 46 is fixed to the lower surface of the main plate 43 so as to be disposed at a predetermined interval from the main plate 43 and cover the cooling air holes.
  • a plurality of guide blades 46 a extending radially are provided on the surface of the main plate cover 46 that faces the main plate 43.
  • the side plate 45 has an outer diameter Da.
  • the side plate 45 has a shape that gradually decreases from the outer periphery toward the central opening.
  • the side plate 45 is a bell-shaped resin member that protrudes toward the air inlet 31.
  • FIG. 6 is a side view of the blade 44 as seen from the direction of the suction surface, for example.
  • FIG. 7 is a projection view of the blade 44 of FIG. 6 as viewed from above.
  • FIG. 8 is a perspective view of the blade 44 of FIG.
  • FIG. 9 is a side view in which a plurality of cutting lines 10A-10A to 10E-10E are entered from the lower part to the upper part (the end part on the main plate 43 side to the end part on the side plate 45 side) of the blade 44 in FIG. 10A to 10E are cross-sectional views taken along lines 10A-10A to 10E-10 in FIG. 9, respectively.
  • FIG. 11 is a cross-sectional view of the main part showing the characteristics of the blade 44 (difference from the conventional shape of FIGS. 25 to 32) (contrast with the cross-sectional view taken along the line 31B-31B in FIGS. 10 and 31). .
  • Each of the blades 44 is a resin member formed separately from the main plate 43 and the side plate 45 described above. One end surface of each blade 44 is fixed to the main plate 43, and the other end surface of each blade 44 is fixed to the side plate 45. In the side view of the impeller 42, each blade 44 is inclined with the end on the side plate 45 side inclined behind the end on the main plate 43 side as shown in FIG. 28. Further, as shown in FIG. 29, each blade 44 is formed so that these end portions intersect with each other in a substantially X shape. That is, the blade 44 has a three-dimensional shape extending in parallel with the rotation axis while being twisted between the main plate 43 and the side plate 45.
  • An end on the front side in the rotational direction of the blade 44 which is the three-dimensional blade, that is, the front edge 44a extends from the end on the main plate 43 side to a predetermined position on the side plate 45 side so as to have substantially the same radius.
  • the blade 44 has an inclined edge that recedes outward so that the radius gradually decreases from a predetermined position on the side plate 45 side to the side plate 45.
  • an end portion (hereinafter referred to as a trailing edge) 44b in the direction opposite to the rotation direction R side of the blade 44 has a shape different from that of the conventional blade. Unlike the conventional example shown in FIGS.
  • the trailing edge 44b is a straight line (perpendicular to the main plate 43) that extends in parallel with the rotation axis between the end on the main plate 43 side and the end on the side plate 45 side of the blade 44. Does not have a tied shape.
  • the rear edge 44b extends from the end on the side plate 45 side to the end on the main plate 43 side so that the degree of extension increases as the side plate 45 approaches the main plate 43. It is extended to the rear of the air flow.
  • the diameter of the centrifugal fan of the main flow F 1 is the radial length of the edge 44b after the main plate 43 side of the blade 44 to pass (Rb 'in FIG.
  • the edge 44b after the side plate 45 side of the blade 44 It is set longer than the length in the direction (Ra in FIG. 5). Thereby, the velocity distribution of the air flow in the span direction of the blade 44 is effectively developed in the portion on the main plate 43 side where the flow rate is large.
  • the extension of the trailing edge 44b is performed without changing the basic blade surface shape of the three-dimensional blade, and is performed along the same shape.
  • the extension amount of the rear edge 44b is based on the outer diameter Db ′ (FIG. 12) of the enlarged main plate 43 based on the outer diameter Db of the original main plate 43 (the outer diameter Da of the side plate 45).
  • the outer diameter Db is preferably 10% or less of the outer diameter Db.
  • the extension amount of the trailing edge 44b is preferably 10% or less of the outer diameter Da of the side plate 45.
  • the outer diameter Db ′ of the main plate 43 is enlarged by, for example, about 5% with respect to the outer diameter Db of the conventional main plate 43 shown in FIGS.
  • the blade 44 of the present embodiment has a shape in which the mounting position on the rear edge 44b side swells in the rotational direction, as shown in the perspective view of FIG.
  • the outer diameter of the main plate 43 is also increased in accordance with the increase in the radius of the end of the blade 44 on the main plate 43 side. In this way, in correspondence with the extension of the length of the rear edge 44b of the blade 44, the outer diameter of the main plate 43 is also extended, so that the structural strength of the impeller 42 of the centrifugal fan can be improved at the same time. it can.
  • the velocity distribution of the main flow F 1 flowing in the vicinity of the main plate 43 is greatly improved as compared to the flow F 2 in the vicinity of the side plate 45. Therefore, the static pressure-flow rate characteristic (PQ characteristic) of the blade 44 is improved in the entire flow rate range, and the air flow rate is increased.
  • the specific noise characteristics are greatly improved, and the influence of the wake vortex generated at the trailing edge 44b of the three-dimensional blade 44 on the main plate 43 side can be relatively reduced. As a result, noise caused by the wake vortex is effectively reduced.
  • the rear edge 44b extended rearward as it approaches the main plate 43 is extended so as to gradually become longer from the side plate 45 to the main plate 43 as shown in FIG. That is, the shape of the rear edge 44 b of the blade 44 has a taper shape that is expanded in a straight line from the side plate 45 to the main plate 43. Thereby, the velocity distribution at the outlet of the blade 44 is effectively developed in the main flow F 1 . Therefore, the influence of the wake generated at the trailing edge 44b of the blade 44 on the main plate 43 side is relatively weakened.
  • the trailing edge 44b is enlarged with a tapered shape, to changes in the velocity distribution of the main flow F 1 flow rate increases toward the main plate 43, the trailing edge 44b becomes a more suitable shape ing. That is, the shape of the blade 44 can be optimized with respect to the velocity distribution of the airflow, and the fan performance can be further improved.
  • the centrifugal blower of the present embodiment it is possible to realize a small-sized air conditioner with a large air volume and high silence at low cost.
  • the blade 44 is a three-dimensionally shaped blade as described above (see FIGS. 7 and 8). Therefore, the load distribution on the surface of the blade 44 and the pressure fluctuation of the airflow passing between the blades 44 are greatly improved as compared with the blade shape made on the basis of the conventional planarly drawn blade element.
  • Patent Document 3 discloses a blade that is shortened by cutting out a portion on the side plate side. Thereby, the separation of the airflow in the portion on the side plate side of the blade is suppressed, and the velocity distribution at the outlet of the blade is made uniform.
  • the notch is formed in the side plate side portion of the blade, the length of the blade is relatively shorter than the blade without the notch. Therefore, the amount of work that the blades give to the airflow is reduced. In the present embodiment, the blades 44 themselves are not shortened. On the contrary, since the area of the blade 44 is increased, there is no such drawback, and the work amount of the blade 44 is effectively increased.
  • the above technique is effective in a centrifugal fan whose blade width is sufficiently small with respect to the outer shape, as described in Patent Document 3. That is, by cutting out the blade, it is possible to prevent the suction airflow from separating at the side plate side portion of the blade, and to flow the airflow along the side plate side portion of the blade.
  • the above technique is not necessarily effective.
  • the blades are arranged so as to be orthogonal to the main plate and the side plate, there is a technique for changing the thickness of the blade from the end surface on the main plate side of the blade to the end surface on the side plate side of the blade.
  • wing is suppressed.
  • the outer diameter of the blade on the main plate side and the outer diameter of the blade on the side plate side are not the same, and the blade shape is enlarged as it approaches the main plate (for example, see Patent Document 4). reference).
  • flow speed fluctuations in the blade wake are suppressed.
  • the ratio of the diameter at the end face on the main plate side of the impeller / the diameter at the end face on the side plate side of the impeller is set to 1.2 to 1.6. Therefore, when the extension amount due to the expansion of the blades is small, the noise reduction effect cannot be obtained, and conversely, when the extension amount is too large, the flow rate characteristic is deteriorated.
  • the rear edge 44b extended backward as it approaches the main plate 43 is extended from the side plate 45 to the main plate 43 little by little as shown in FIG.
  • the shape of the rear edge 44 b of the blade 44 becomes a substantially tapered shape that is enlarged from the side plate 45 to the main plate 43.
  • the trailing edge 44 b has a more suitable shape with respect to the change in the velocity distribution of the main flow F 1 that flows in the vicinity of the main plate 43.
  • the outer diameter of the main plate 43 is also increased in accordance with the increase in the radial length of the rear edge 44b of the blade 44 on the main plate 43 side.
  • Example c in the blade 44 according to the present embodiment, the expansion ratio of the outer diameter Db ′ of the main plate 43 (the extension ratio of the width of the rear edge portion 44b to the rear of the air flow) is 5%.
  • Example d is an impeller provided with a three-dimensional blade in which the enlargement ratio of the outer diameter Db ′ of the main plate 43 is 10% in the blade 44 of the present embodiment.
  • Conventional Example a is an impeller using the conventional blades shown in FIGS.
  • Conventional example b is obtained by enlarging the entire diameter of the fan of conventional example a by 5%.
  • Examples c and d for example, as shown in FIG.
  • the characteristics of these Examples c and d are clearly improved as compared with the conventional example b in which the fan diameter is uniformly expanded as a whole.
  • the shape of the rear edge 44b of the blade 44 that expands (extends) the main plate 43 is not limited to the linearly expanded shape (linear taper shape) as described above.
  • it may be a quadratic curve shape that draws a parabola as shown in FIG.
  • the curved shape of the trailing edge 44b takes into account the deviation of the wind speed distribution of the airflow blown from the impeller, and the trailing edge 44b of the blade 44 is extended more in the radial direction as it approaches the main plate 43 than the side plate 45. Become.
  • the shape of the trailing edge 44 b of the blade 44 becomes a quadratic function taper shape that expands in an arc shape from the side plate 45 to the main plate 43.
  • the trailing edge 44b of the blade 44 can be made more suitable for the velocity distribution of the main flow F 1 that flows in the vicinity of the main plate 43 as shown in FIG.
  • the rear edge 44b is formed so that one or more inflection points exist in the curved portion. Thereby, the rear edge 44b has a bulging portion in the vicinity of the main plate 43.
  • the enlargement of the rear edge 44b of the end surface of the main plate 43 is set slightly shorter than the maximum extension portion (however, at least the radius of the end portion of the rear edge 44b on the side plate 45 side).
  • the front edge 44 a of the blade 44 further includes first and second protrusions that project in a stepped manner toward the inside of the impeller 42 (in this embodiment, two stepped portions). Steps 44c and 44d may be provided. In the first and second sets of step portions 44c and 44d, the airflow sucked into the impeller 42 through the air inlet 31 and the bell mouth 5 of FIG. In this case, the blade 44 has a function of suppressing separation from the suction surface side. Thereby, the 1st and 2nd step parts 44c and 44d are contributing to making the blowing noise of the air blower 4 still smaller.
  • the negative pressure surface refers to the surface of the blade 44 facing the inner peripheral side of the impeller 42, and the surface opposite to the negative pressure surface, that is, the surface of the blade 44 facing the outer peripheral side of the impeller 42 is positive. It is a pressure side.
  • the lengths La ⁇ Lb, Lc ⁇ Ld of the first and second step portions 44c, 44d are 0.09 to 0. 0 of the original chord lengths L 1 , L 2 , L 3 in the span direction of the blade 44. It is set to 18 times. That is, the length of the lower first step portion 44c varies in the span direction in a range of 0.15 (La) to 0.2 (Lb) times, and the length of the upper second step portion 44d is It varies in the range of 0.08 (Lc) to 0.1 (Ld) times.
  • the blade 44 of the third modification is represented as a trapezoid stepped embodiment d. Further, the embodiment shown in FIGS. 1 to 12 where the first and second step portions 44c and 44d are not attached to the front edge 44a described above (this is shown as trapezoidal stepless) c.
  • the comparative example b is provided with first and second step portions 44c and 44d with respect to a conventional blade.
  • Example c is compared with Example d, for example, as shown in FIG. 22, the specific noise characteristic is reduced in the entire flow region. In Example c, a reduction effect of at least 1.1 [dBA] can be obtained particularly at the lowest specific noise point.
  • the centrifugal blower of the present embodiment shown in FIGS. 1 to 12 described above is designed such that the airflow passing through the impeller flows below the blade 44 as compared with the conventional example a. Therefore, the peeling suppression effect by the vertical vortex generated by the first and second step portions 44c and 44d of the front edge 44a is more effectively affected.
  • Example c is inferior in the low air volume region as compared with Comparative Example b.
  • Example d the first and second step portions 44c and 44d were added to improve the characteristics in the low air volume region as compared with Comparative Example b.
  • the aerodynamic characteristic of Example d is also improved in the entire air volume region.
  • the centrifugal blower using the embodiment d according to the invention of the third modification can generate a larger amount of air at the same static pressure.
  • the centrifugal blower of the present modification 3 has a lower specific noise than conventional centrifugal blowers and can increase the air volume even at the same static pressure. This makes it possible to develop a fan that is small and quiet.
  • ⁇ Application object of centrifugal blower of the present invention In general, the deviation of the velocity distribution of the blown airflow in the main plate side portion of the blade as described above is a problem that always occurs in various centrifugal fans. Therefore, the present invention is applicable to the impellers of such various types of centrifugal blowers (for example, turbo type, sirocco type, radial type, etc.). In that case, the fan characteristics can be improved sufficiently effectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un ventilateur centrifuge (1) comportant des aubes tridimensionnelles (44), une plaque principale (43) sur laquelle une surface d'extrémité de chaque aube (44) est, par rapport à la direction d'extension de celle-ci, fixée avec des intervalles circonférentiels prédéterminés entre chaque aube (44), une plaque latérale de forme annulaire (45) montée sur l'autre surface d'extrémité de chaque aube (44) par rapport à la direction d'extension de celle-ci, et un moteur (41) pour faire tourner les aubes (44) via la plaque principale (43). La longueur radiale de cette partie du bord arrière (44b) de chaque aube (44) se trouvant sur le côté de la plaque principale (43) est définie pour être supérieure à la longueur radiale de la partie du bord arrière (44b) se trouvant sur le côté de la plaque latérale (45).
PCT/JP2009/058938 2008-05-14 2009-05-13 Ventilateur centrifuge WO2009139422A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US12/921,828 US20110023526A1 (en) 2008-05-14 2009-05-13 Centrifugal fan
JP2010512006A JPWO2009139422A1 (ja) 2008-05-14 2009-05-13 遠心送風機
EP09746628A EP2275689A1 (fr) 2008-05-14 2009-05-13 Ventilateur centrifuge
AU2009247219A AU2009247219A1 (en) 2008-05-14 2009-05-13 Centrifugal fan
CN2009801123504A CN101990604A (zh) 2008-05-14 2009-05-13 离心鼓风机

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JP2008-126940 2008-05-14
JP2008126940 2008-05-14

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WO2009139422A1 true WO2009139422A1 (fr) 2009-11-19

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US (1) US20110023526A1 (fr)
EP (1) EP2275689A1 (fr)
JP (1) JPWO2009139422A1 (fr)
KR (1) KR20100134011A (fr)
CN (1) CN101990604A (fr)
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US20110286848A1 (en) * 2010-05-19 2011-11-24 The New York Blower Company Industrial fan impeller having a tapered blade and method
WO2014061094A1 (fr) * 2012-10-16 2014-04-24 三菱電機株式会社 Réacteur à double flux et appareil de conditionnement d'air
CN104279188A (zh) * 2014-10-29 2015-01-14 珠海格力电器股份有限公司 离心式风机及具有其的空调器
WO2015170401A1 (fr) * 2014-05-09 2015-11-12 三菱電機株式会社 Soufflante centrifuge et aspirateur électrique
WO2020080260A1 (fr) * 2018-10-15 2020-04-23 日立建機株式会社 Engin de chantier
JPWO2019106761A1 (ja) * 2017-11-29 2020-07-02 三菱電機株式会社 遠心ファンおよび回転電機
WO2020161850A1 (fr) * 2019-02-07 2020-08-13 三菱電機株式会社 Soufflante d'air centrifuge et climatiseur utilisant celle-ci
JPWO2023007713A1 (fr) * 2021-07-30 2023-02-02
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JP5783214B2 (ja) * 2013-09-30 2015-09-24 ダイキン工業株式会社 遠心送風機及びこれを備えた空気調和機
KR20160063743A (ko) * 2014-11-27 2016-06-07 삼성전자주식회사 원심송풍기용 팬조립체 및 이를 구비한 공기조화장치
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JP6621194B2 (ja) * 2015-06-03 2019-12-18 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． ターボファン及びこのターボファンを用いた送風装置
ITUB20152807A1 (it) * 2015-08-03 2017-02-03 Ma Ti Ka S R L Ventola per forni per la cottura di alimenti
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EP3647603A1 (fr) 2018-10-31 2020-05-06 Carrier Corporation Agencement de roue centrifuge d'un ventilateur pour réduire le bruit
JP7040493B2 (ja) * 2019-04-25 2022-03-23 株式会社デンソー 遠心ファンおよびその遠心ファンを備えた送風機
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CN114321005B (zh) * 2022-03-01 2022-05-13 佛山市南海九洲普惠风机有限公司 一种低噪前弯离心风机叶轮

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US20110286848A1 (en) * 2010-05-19 2011-11-24 The New York Blower Company Industrial fan impeller having a tapered blade and method
US9004868B2 (en) * 2010-05-19 2015-04-14 The New York Blower Company Industrial fan impeller having a tapered blade and method
WO2014061094A1 (fr) * 2012-10-16 2014-04-24 三菱電機株式会社 Réacteur à double flux et appareil de conditionnement d'air
WO2014061642A1 (fr) * 2012-10-16 2014-04-24 三菱電機株式会社 Réacteur à double flux et climatiseur
CN104736854A (zh) * 2012-10-16 2015-06-24 三菱电机株式会社 涡轮风扇及空调机
JP5955402B2 (ja) * 2012-10-16 2016-07-20 三菱電機株式会社 ターボファンおよび空気調和機
JPWO2014061642A1 (ja) * 2012-10-16 2016-09-05 三菱電機株式会社 ターボファンおよび空気調和機
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WO2015170401A1 (fr) * 2014-05-09 2015-11-12 三菱電機株式会社 Soufflante centrifuge et aspirateur électrique
TWI573551B (zh) * 2014-05-09 2017-03-11 Mitsubishi Electric Corp Centrifugal blowers and electric vacuum cleaners
JPWO2015170401A1 (ja) * 2014-05-09 2017-04-20 三菱電機株式会社 遠心送風機及び電気掃除機
CN104279188A (zh) * 2014-10-29 2015-01-14 珠海格力电器股份有限公司 离心式风机及具有其的空调器
JP7062684B2 (ja) 2017-11-29 2022-05-06 三菱電機株式会社 遠心ファンおよび回転電機
JPWO2019106761A1 (ja) * 2017-11-29 2020-07-02 三菱電機株式会社 遠心ファンおよび回転電機
JP2020063683A (ja) * 2018-10-15 2020-04-23 日立建機株式会社 建設機械
WO2020080260A1 (fr) * 2018-10-15 2020-04-23 日立建機株式会社 Engin de chantier
JP7207933B2 (ja) 2018-10-15 2023-01-18 日立建機株式会社 建設機械
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WO2020161850A1 (fr) * 2019-02-07 2020-08-13 三菱電機株式会社 Soufflante d'air centrifuge et climatiseur utilisant celle-ci
JPWO2020161850A1 (ja) * 2019-02-07 2021-09-30 三菱電機株式会社 遠心送風機及びそれを用いた空気調和機
JP7003301B2 (ja) 2019-02-07 2022-01-20 三菱電機株式会社 遠心送風機及びそれを用いた空気調和機
JPWO2023007713A1 (fr) * 2021-07-30 2023-02-02
WO2023007713A1 (fr) * 2021-07-30 2023-02-02 三菱電機株式会社 Impulseur, et soufflante centrifuge
JP7482332B2 (ja) 2021-07-30 2024-05-13 三菱電機株式会社 羽根車及び遠心送風機
WO2023032762A1 (fr) * 2021-09-02 2023-03-09 株式会社デンソー Ventilateur centrifuge

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US20110023526A1 (en) 2011-02-03
CN101990604A (zh) 2011-03-23
AU2009247219A1 (en) 2009-11-19
EP2275689A1 (fr) 2011-01-19
KR20100134011A (ko) 2010-12-22
JPWO2009139422A1 (ja) 2011-09-22

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