WO2009139422A1 - 遠心送風機 - Google Patents
遠心送風機 Download PDFInfo
- 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
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- WO
- WIPO (PCT)
- Prior art keywords
- blade
- main plate
- centrifugal blower
- air
- impeller
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—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
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- 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
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- 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
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- 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
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- 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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Abstract
Description
このような三次元形状の羽根を採用した羽根車によると、上述のような二次元形状の羽根を採用したものと比較して、羽根の表面における負荷分布および羽根の間を通過する気流の圧力変動が改善される。
先ず図25は、羽根車を有する遠心送風機を採用した空気調和装置1を示す。この空気調和装置1は、天井埋込型の空気調和装置であり、内部に各種部品を収納するケーシング2と、そのケーシング2の下側に配置された化粧パネル3とを備えている。より具体的には、空気調和装置1のケーシング2は、空調室の天井Uに形成された開口内に挿入され、化粧パネル3が天井Uに沿うように配置されている。
上記の課題を解決するため、本発明の一態様によれば、三次元形状の複数の羽根と、該複数の羽根を周方向に所定の間隔をおいて各羽根のスパン方向の一端面を固定する主板と、前記各羽根のスパン方向の他端面に設けられたリング状の側板と、前記主板を介して前記羽根を回転させる羽根駆動手段とを備える遠心送風機であって、前記各羽根の前記主板側の外周端部の径方向の長さは、各羽根の側板側の外周端部の径方向の長さよりも長く設定される遠心送風機が提供される。
このような構成によると、羽根の後縁の形状が側板から主板にかけて拡大される略テーパ形状となる。そのため、羽根の後縁の形状は、羽根の主板側の部分に偏って流れる主流の速度分布の変化に応じた適切なものにすることができる。そして、この側板から主板にかけて徐々に拡大される略テーパ形状は、直線的に変化するものでも、また曲線状に変化するものの何れでもかまわない。
遠心送風機は主板近傍の気流が、主板の壁面による粘性の影響で層流せん断層を形成する。これにより、主流の流路が狭まり、ファン性能が低下する恐れがある。ところが、上記の構成によれば、上記せん断層の発達を抑制し、ファン性能を向上させることができる。
このような構成によれば、延長された後縁の形状を、より主流の速度分布の変化に応じた適切なものにすることができ、さらなるファン性能の向上を図ることができる。
このような構成にすれば、空気吸入口を通して羽根車内に吸入された気流が羽根の後縁から外方へ吹き出される際に、羽根の負圧面側から剥離する気流を効果的に抑制することができる。それによって、上記送風機の騒音をさらに有効に低減することができる。
羽根の後縁の長さの延長に対応して、さらに、主板の径も合わせて延長することにより、遠心送風機の羽根車の構造上の強度をも同時に向上させることができる。
空気調和機用室内機の送風機では、その特性上、本質的に大風量および静音性が要求される。したがって、小型で送風性能が高く、騒音が低い本発明の遠心送風機は、空気調和機用室内機の送風機として最適である。
(1)空気調和装置の全体構成
図1は、本発明の一実施の形態にかかる遠心送風機を採用する空気調和装置1を示す外観斜視図(天井部は省略)を示す。この空気調和装置1は、天井埋込型の空気調和装置であり、内部に各種部品を収納するケーシング2と、そのケーシング2の下側に配置された化粧パネル3とを備えている。より具体的には、上記空気調和装置1のケーシング2は、例えば図2(当該空気調和装置1の縦断面図)に示されるように、空調室の天井Uに形成された開口内に挿入され、上記化粧パネル3が天井Uに沿うように配置されている。
次に、上記遠心送風機4の羽根車42の構造について、図2~図5を参照して詳しく説明する。ここで、図3は、同羽根車42の外観を示す斜視図である。また、図4は、同図3の羽根車42を示す側面図である。さらに、図5は、同図4のように設置された羽根車42を上方から見た図である。
次に、上記羽根車42の各ブレード44の構造について、図6~図11を参照して詳しく説明する。ここで、図6は、同ブレード44を例えば負圧面の方向から見た側面図である。また、図7は、同図6のブレード44を上方から見た投影図である。図8は、図6のブレード44を左斜め後方上部から見た斜視図である。図9は、同図6のブレード44の下部から上部(主板43側端部から側板45側の端部)にかけて複数の切断線10A-10A~10E-10Eを入れた側面図である。図10(a)~図10(e)は、それぞれ図9の10A-10A線~10E-10線に沿った断面図である。図11は、同ブレード44の特徴(図25~図32の従来形状との相違)を示す要部の断面図(図10、図31の31B-31B線に沿った断面図を対比)である。
また、後縁44bを延長する際、ブレード44の主板43側の翼素の入口角・出口角・取付角・スキュー角は、図28~図32の元のブレード44の値を保たれる。したがって、本実施の形態のブレード44は、例えば図8の斜視図で示すように後縁44b側の取付位置が回転方向に膨らむ形状となる。
このようにブレード44の後縁44bの長さの延長に対応して、さらに主板43の外径も合わせて延長するため、遠心送風機の羽根車42の構造上の強度をも同時に向上させることができる。
特に、本実施形態の遠心送風機の羽根車では、そのブレード44が、上述のような三次元形状の翼(図7、図8参照)である。そのため、従来の平面的に描かれた翼素を基礎に作られたブレード形状と比較して、ブレード44の表面における負荷分布及びブレード44間を通過する気流の圧力変動が大きく改善される。
特に、本実施の形態では、上記主板43に近づくほど後方に延長された後縁44bは、図12の如く側板45から主板43にかけて少しずつ長くなるように延長されている。
今、2つの従来例a,b及び本発明に係る2つの実施例c,dを用いて、そられ例の送風特性を確認した。実施例cは、上記本実施の形態のブレード44において、その主板43の外径Db′の拡大率(後縁部44bの幅の空気流後方への延長率)を、5%とした三次元翼を備える羽根車である。実施例dは、上記本実施の形態のブレード44において、その主板43の外径Db′の拡大率を10%とした三次元翼を備える羽根車である。比較例として、従来例aは、図27~図32に示す従来のブレードを用いた羽根車である。従来例bは、従来例aのファンの直径全体を5%拡大したものである。
なお、上記ブレード44の後縁44bの主板43への拡大(延長)する形状は、上述のような直線的に拡大した形状(一次関数的なテーパ形状)に限らない。例えば、図16のような放物線を描くような2次関数的な曲線形状であっても良い。
<変形例2>
上述のような遠心送風機は、主板43近傍の気流が、主板43の壁面による粘性の影響で層流せん断層を形成する。これによって主流F1の流路が狭まり、ファン性能が低下するおそれがある。
<変形例3>
ブレード44の前縁44aには、さらに図18~図21に示すように羽根車42の内方に向かって階段状(本実施形態では、段部が2段)に突出する第1及び第2の段部44c,44dが設けられてもよい。こられ第1及び第2の2組の段部44c,44dは、上記図1の空気吸入口31及びベルマウス5を通じて羽根車42内に吸入された気流がブレード44によって外方に吹き出される際に、ブレード44の負圧面側から剥離するのを抑える機能を有している。それにより、第1及び第2の段部44c,44dは、送風機4の吹出騒音を、さらに小さくするのに寄与している。
<変形例4>
なお、変形例3の第1及び第2の段部44c,44dは、例えば図24に示すように、上述の変形例2と組み合わせることもできる。
一般に、上述のようなブレードの主板側の部分における吹出気流の速度分布の偏りは、各種の遠心送風機に必ず発生している問題である。そのため、本発明は、そのような各種のタイプの遠心送風機(例えばターボ型、シロッコ型、ラジアル型など)の羽根車に対して適用可能である。その場合、十分に有効にファン特性を改善することができる。
Claims (10)
- 三次元形状の複数の羽根と、該複数の羽根を周方向に所定の間隔をおいて各羽根のスパン方向の一端面を固定する主板と、前記各羽根のスパン方向の他端面に設けられたリング状の側板と、前記主板を介して前記羽根を回転させる羽根駆動手段とを備える遠心送風機であって、前記各羽根の前記主板側の外周端部の径方向の長さは、同羽根の側板側の外周端部の径方向の長さよりも長く設定される遠心送風機。
- 前記各羽根の前記主板側の外周端部の径方向の長さを、同羽根の側板側の外周端部の径方向の長さよりも長く設定することにより、前記各羽根を通過する気流が、前記羽根の主板側の部分で有効にその羽根から仕事を受けられ、かつ前記各羽根のスパン方向における気流の速度が前記各羽根の前記主板側の部分で有効に発達させる請求項1記載の遠心送風機。
- 上記各羽根の前記主板側の外周端部の径方向の長さは、同羽根の後縁を気流後方に向かって延長することにより、前記各羽根の前記側板側の外周端部の径方向の長さよりも長く形成されている請求項1又は2記載の遠心送風機。
- 前記後縁は、前記側板から前記主板に近づくに従って徐々に長くなるように延長されている請求項3記載の遠心送風機。
- 前記後縁は、曲線状に延長されるとともに、同曲線部に一つ以上の変曲点が存在するように、前記後縁には前記主板側の部分に膨出部が形成される請求項4記載の多翼遠心送風機。
- 前記後縁は、同後縁における前記気流の主流の速度分布に対応して後方に長く延長されている請求項3記載の遠心送風機。
- 前記後縁の延長量は、前記側板の外径の10%以下である請求項6に記載の遠心送風機。
- 前記各羽根の前縁の前記主板側の部分に、その羽根の前方へ所定の長さ延長された段部が設けられる請求項1~7の何れか1項に記載の遠心送風機。
- 前記主板の外径が前記羽根の延長に合わせて拡大される請求項1~8の何れか1項に記載の遠心送風機。
- 前記遠心送風機が、空気調和機用室内機の送風機として構成される請求項1~9の何れか1項に記載の遠心送風機。
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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 (en) | 2008-05-14 | 2009-05-13 | Centrifugal fan |
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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EP (1) | EP2275689A1 (ja) |
JP (1) | JPWO2009139422A1 (ja) |
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CN (1) | CN101990604A (ja) |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
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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 (ja) * | 2012-10-16 | 2014-04-24 | 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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Also Published As
Publication number | Publication date |
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JPWO2009139422A1 (ja) | 2011-09-22 |
KR20100134011A (ko) | 2010-12-22 |
EP2275689A1 (en) | 2011-01-19 |
CN101990604A (zh) | 2011-03-23 |
US20110023526A1 (en) | 2011-02-03 |
AU2009247219A1 (en) | 2009-11-19 |
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